WO2022017463A1 - 自动变速器高压系统的压力控制方法 - Google Patents

自动变速器高压系统的压力控制方法 Download PDF

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WO2022017463A1
WO2022017463A1 PCT/CN2021/107859 CN2021107859W WO2022017463A1 WO 2022017463 A1 WO2022017463 A1 WO 2022017463A1 CN 2021107859 W CN2021107859 W CN 2021107859W WO 2022017463 A1 WO2022017463 A1 WO 2022017463A1
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pressure
oil pump
max
electric oil
value
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PCT/CN2021/107859
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English (en)
French (fr)
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叶珂羽
陈建勋
刘振宇
顾强
唐立中
康志军
吴世楠
宋建军
赵慧超
赵雪松
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中国第一汽车股份有限公司
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Publication of WO2022017463A1 publication Critical patent/WO2022017463A1/zh

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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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal

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  • the present application relates to the technical field of transmissions, for example, to a pressure control method for a high-pressure system of an automatic transmission.
  • the high and low pressure system is divided into two structures, in which the low pressure system is used for cooling and lubrication, the high pressure system is used for the control of the clutch, shifting, and parking mechanism, and the electric oil pump is used for the high and low pressure system. Hydraulic oil is supplied on demand to effectively improve the working efficiency of the automatic transmission.
  • the high-pressure system sets the accumulator in the main oil circuit to store the pressure value, and then controls the opening or closing of the electric oil pump, so that the pressure value of the main oil circuit is always kept at the upper limit of the pressure of the main oil circuit. value and the lower limit of pressure to ensure the action requirements of the clutch actuator or shift actuator to meet the functional requirements of the high-pressure system, and it is not necessary to keep the electric oil pump in a working state all the time.
  • the pressure upper limit value and the pressure lower limit value in the high-pressure system are fixed values respectively. Since the pressure value of the main oil circuit is greatly affected by various factors such as temperature and oil volume, it is very difficult to meet the conditions of various factors. It is easy to cause the pressure range between the fixed pressure upper limit value and the fixed pressure lower limit value to be small, so that the adjustable range of the pressure value of the main oil circuit is small, resulting in a high frequency of starting the electric oil pump, which cannot be adjusted according to the actual demand. Controlling the pressure adjustment range is not conducive to the improvement of the overall working efficiency of the automatic transmission.
  • the present application proposes a pressure control method for a high-pressure system of an automatic transmission, which can adjust the pressure range of the main oil circuit of the high-pressure system in real time, so that the working efficiency of the high-pressure system is high.
  • a pressure control method for a high pressure system of an automatic transmission comprising:
  • T is the temperature
  • ⁇ p(T) Max ⁇ p 1 (T), ⁇ p 2 (T) ⁇ , ⁇ p(T) is the pressure value to be increased in the main oil circuit at different temperatures, ⁇ p 1 (T) is the pressure value at p(T) , the clutch actuator operation is performed once the need to increase the high pressure main oil passage of the hydraulic oil pressure, ⁇ p 2 (T) is in the p (T), said shift actuator means performing an action for an increase in a main oil passage The pressure value of the high pressure hydraulic oil;
  • P out-max is the maximum output power of the motor driving the electric oil pump 3
  • the unit is W
  • q is the displacement of the electric oil pump
  • the unit is mL/rev
  • ⁇ max is the maximum speed of the electric oil pump
  • the unit is rev /min
  • ⁇ (T, ⁇ max , p) is the total efficiency of the electric oil pump at the maximum speed
  • p is the back pressure of the electric oil pump
  • the unit is Mpa;
  • p max2 p(T)+ ⁇ p N (T,N)
  • N is the number of actions of the clutch actuator or the shift actuator
  • ⁇ p N (T, N) is the maximum number of actions at different temperatures
  • the lower limit value p min and the upper limit value p max are calculated the number of times N; and
  • the control module controls the control module according to the relationship between p 0 and p min and p max.
  • the stop or operation of the electric oil pump realizes the control of the pressure of the main oil circuit.
  • control module controlling the stop or operation of the electric oil pump according to the relationship between p 0 and p min and p max includes:
  • control module controls the electric oil pump to start running, and when p 0 ⁇ p max , the control module controls the electric oil pump to stop running.
  • the hydraulic power P 1 output by the electric oil pump is:
  • P out is the output power of the motor that drives the electric oil pump 3, (unit: W)
  • ⁇ is the rotational speed of the electric oil pump 3 (unit: rev/min)
  • the formula (1) can be converted to obtain:
  • control module controls the electric oil pump to operate at a rotational speed of
  • t 1 is the time required for the pressure value on the main oil circuit to change from 0 to the preset calibration test pressure value when the electric oil pump is running;
  • ⁇ max (T) is the time required to meet the NVH performance requirements at different temperatures
  • the maximum rotational speed of the electric oil pump, ⁇ min (T, t 1 ) is the lower limit of the rotational speed of the electric pump at different temperatures T in the time period of 0-t 1.
  • p(T), ⁇ p 1 (T), and ⁇ p 2 (T) are obtained through experiments.
  • the total efficiency ⁇ (T, ⁇ max ,p) of the electric oil pump includes the mechanical efficiency and volumetric efficiency of the electric oil pump at the maximum speed, ⁇ (T, ⁇ max ,p) is obtained through a lookup table get.
  • ⁇ p N (T,N) is obtained through a look-up table.
  • the rotational speed ⁇ min (T, t 1 ) and the rotational speed ⁇ max (T) of the electric oil pump are obtained through experiments.
  • the high-pressure system includes an electronically controlled on-off valve
  • the control module controls the stop or operation of the electric oil pump according to the relationship between p 0 and p min and p max, including: the control module may: By controlling the electronically controlled switch valve in the high-pressure system, the main oil circuit is disconnected or connected to the main oil circuit, so as to control the stop or operation of the electric oil pump.
  • FIG. 1 is a schematic structural diagram of an automatic transmission high-voltage system provided in Embodiment 1 of the present application;
  • FIG. 2 is a schematic flowchart of a pressure control method for an automatic transmission high-pressure system provided in Embodiment 2 of the present application;
  • FIG. 3 is a schematic flowchart of a pressure control method for a high pressure system of a moving transmission provided by an embodiment.
  • an automatic transmission high-pressure system is proposed.
  • the automatic transmission high-pressure system is used for the control of the clutch, gear shift, and parking mechanism, so as to provide high-pressure hydraulic oil for the clutch control oil circuit 8 and the shift control oil circuit 9 respectively. , to meet the functional requirements of clutch and gear shifting.
  • the automatic transmission high-pressure system includes an oil tank 1 for storing hydraulic oil, an electric oil pump 3 , a filter 4 and an accumulator 7 , which are sequentially arranged on the main oil circuit 10 .
  • the accumulator 7 is respectively connected with the clutch control oil circuit 8 and the shift control oil circuit 9.
  • the accumulator 7 is arranged to convert the pressure in the main oil circuit 10 into compression energy and store it.
  • the main oil circuit 10 needs pressure
  • the accumulator 7 can convert the compression energy into pressure energy and release it to resupply the clutch control oil circuit 8 or the shift control oil circuit 9 .
  • the filter 4 is arranged to filter impurities in the hydraulic oil pumped by the electric oil pump 3 in the oil tank 1, and a check valve 5 is arranged between the filter 4 and the accumulator 7 to prevent the hydraulic pressure in the main oil circuit 10.
  • the oil is returned to the oil tank 1; a pressure sensor 6 is arranged between the one-way valve 5 and the accumulator 7 to monitor the pressure value p 0 of the main oil circuit 10 in the high-pressure system in real time, and a temperature sensor is arranged in the oil tank 1 2, to detect the temperature T of the hydraulic oil in the oil tank 1 in real time.
  • the automatic transmission high-voltage system further includes a control module (not shown in the figure), the control module is respectively connected with the temperature sensor 2, the pressure sensor 6 and the electric oil pump 3 for control; The temperature value and the pressure value of the pressure sensor 6 are used to control the operation or stop of the electric oil pump 3 according to the temperature value and the pressure value.
  • the control module in this embodiment is a common control module in the related art, therefore, the specific structure and working principle of the control module will not be described in detail here.
  • the electric oil pump 3 is a single pump. In other embodiments, the electric oil pump 3 may also be a double pump.
  • This embodiment proposes a pressure control method for the high pressure system of the automatic transmission in the first embodiment, which can control the pressure upper limit value p max and the pressure lower limit value p min on the main oil circuit 10 in the high pressure system in real time, so that the control Larger and more precise.
  • the pressure control method of the high pressure system of the automatic transmission includes the following steps:
  • p(T) is the pre-charge pressure of the accumulator 7 at different temperatures
  • T is the temperature
  • p(T) is the characteristic of the accumulator 7 itself, and the specific relationship of p(T) can be obtained through experiments;
  • ⁇ p(T) Max ⁇ p 1 (T), ⁇ p 2 (T) ⁇ , that is, the value of ⁇ p (T) is the larger one of ⁇ p 1 (T) and ⁇ p 2 (T), ⁇ p( T) is the pressure value that the main oil circuit 10 needs to increase at different temperatures, ⁇ p 1 (T) is the pressure value of the high-pressure hydraulic oil that the main oil circuit 10 needs to increase when the clutch actuator performs one action at p(T), ⁇ p 2 (T) is the pressure value of the high-pressure hydraulic oil that needs to be increased in the main oil circuit 10 when the shift actuator performs one action under p(T).
  • ⁇ p (T) is the larger one of ⁇ p 1 (T) and ⁇ p 2 (T), which can ensure that when the pressure of the main oil circuit 10 is at the lowest level, if the clutch actuator or the shift actuator has an action According to the requirement, the storage amount of the accumulator 7 can ensure at least one action of the clutch actuator or the shift actuator, so as to give the electric oil pump 3 a time margin for restarting.
  • the specific relational expressions of ⁇ p 1 (T) and ⁇ p 2 (T) can be obtained through experiments.
  • P out-max is the maximum output power of the motor driving the electric oil pump 3
  • the unit is W, which is a known fixed value
  • q is the displacement of the electric oil pump 3
  • the unit is mL/rev, which is a known fixed value
  • ⁇ max is The maximum speed of the electric oil pump 3, the unit is rev/min
  • ⁇ (T, ⁇ max ,p) is the total efficiency of the electric oil pump 3 at the maximum speed
  • p is the back pressure of the electric oil pump 3
  • the unit is MPa (Mpa) ;
  • the total efficiency ⁇ (T, ⁇ max , p) of the electric oil pump 3 includes the mechanical efficiency and volumetric efficiency of the electric oil pump 3 at the maximum speed
  • p max2 p(T)+ ⁇ p N (T,N)
  • N is the number of actions of the clutch actuator or shift actuator
  • ⁇ p N (T,N) is the main oil circuit under the maximum number of actions at different temperatures 10
  • the pressure value to be increased; ⁇ p N (T, N) can be obtained through the test to obtain the relationship table between ⁇ p N (T, N) and T and N respectively, and the current temperature T can be obtained by querying the relationship table obtained by the test and ⁇ p N (T,N) under N, and the specific relationship of p(T) can be obtained through experiments, so as to obtain the specific value of p max2.
  • P out is the output power of the motor driving the electric oil pump 3, (unit: W)
  • ⁇ is the rotational speed of the electric oil pump 3 (unit: rev/min)
  • the pressure control method for the high pressure system of an automatic transmission further includes the following steps:
  • the control module determines the relationship between p 0 and p min and p max according to p 0 .
  • the relationship between the electric oil pump 3 is controlled to stop or operate to realize the control of the pressure of the main oil circuit.
  • the temperature sensor 2 transmits the detected real-time hydraulic oil temperature T to the control module, and the control module acts according to the received temperature value T and the predetermined clutch actuator or shift actuator.
  • the number of times N respectively calculates the specific values of p min and p max ; finally, the pressure sensor 6 transmits the detected pressure value p 0 of the main oil circuit 10 at this temperature T to the control module, and the control module according to the received p
  • the relationship between 0 and the calculated p min and p max is used to control the stop or operation of the electric oil pump 3, so as to realize the control of the pressure of the main oil circuit.
  • the values of p min and p max are more accurate, and the value range between p min and p max is larger, so that the adjustable range of the pressure value of the main oil circuit 10 is larger and more accurate, so that the electric oil pump 3
  • the frequency of starting is low, and while meeting the functional requirements of the high-pressure system, the pressure range of the main oil circuit 10 of the high-pressure system can be adjusted in real time, and the hydraulic oil supplied on demand can be precisely controlled, so that the overall working efficiency of the automatic transmission is high; and p max selects the smaller value of p max1 and p max2 , and comprehensively considers the requirements on the number of actions of the clutch actuator and the shift actuator in the hydraulic system design index, which can prevent the electric oil pump 3 from running in the limit power area, which may lead to electric The temperature of the oil pump 3 rises rapidly, and it is easy to damage the electric oil pump 3 when running for a long time.
  • the control module controls the electric oil pump 3 to not operate, that is, the pressure value of the main oil circuit 10 can maintain the clutch actuator or the shift actuator at least one action at this time, and the electric oil pump 3 is temporarily not required to supply high-pressure oil .
  • the control module controls the electric oil pump 3 to start running, so as to continuously supply high pressure to the main oil circuit 10 oil to meet the performance requirements of the clutch actuator or shift actuator; until the electric oil pump 3 supplies oil to p 0 ⁇ p max , that is, the pressure of the main oil circuit 10 is sufficient to maintain the clutch actuator or shift actuator.
  • the control module controls the electric oil pump 3 to stop running.
  • control module is directly connected to the electric oil pump 3 to control the stop or operation of the electric oil pump 3 .
  • an electronically controlled on-off valve can also be set between the filter 4 on the main oil circuit 10 and the one-way valve 5, so that the control module is controlled and connected to the electronically controlled on-off valve, so that the control module can control the electronically-controlled on-off valve.
  • the opening and closing of the electric oil pump 3 can be realized or stopped. The specific control method needs to be determined according to the actual work requirements and working conditions.
  • the faster the electric oil pump 3 rotates the faster the oil filling speed and the shorter the oil filling time.
  • Noise, Vibration, Harshness, NVH) performance will deteriorate, and the speed of the electric oil pump 3 is greatly affected by temperature.
  • the control module controls the rotation speed of the electric oil pump 3 to be: Among them, t 1 is the time required for the pressure value on the main oil circuit 10 to change from 0 to the preset calibration test pressure value when the electric oil pump 3 is running, and t 1 can be obtained through experiments.
  • ⁇ max (T) is the maximum rotational speed of the electric oil pump 3 that meets the NVH performance requirements at different temperatures, and ⁇ max (T) can be obtained through experiments. Among them, NVH performance is the most direct and superficial comprehensive factor to measure the quality of automobile manufacturing, and ⁇ min (T, t 1 ) is the lower limit of the electric pump speed under different temperatures T in the time 0-t 1.
  • the temperature sensor 2 transmits the detected real-time temperature T of the hydraulic oil to the control module, and the control module calculates p min , p max and ⁇ at this temperature respectively according to the received temperature value T and the predetermined known value. and the pressure sensor 6 transmits the detected pressure value p 0 of the main oil circuit 10 at this temperature T to the control module, and the control module receives p 0 .
  • the main oil circuit 10 is continuously supplied with high-pressure oil to meet the performance requirements of the clutch actuator or shift actuator; until the control module determines that p 0 ⁇ p max , that is, the main oil
  • the control module will calculate and judge based on the real-time temperature T. p 0 ⁇ p min ; when the control module calculates and judges again that p 0 ⁇ p min , the above control process is repeated to control the pressure of the main oil circuit 10 in the high pressure system of the automatic transmission.
  • p min , p max and ⁇ are changed in real time with changes in real-time oil temperature T and control requirements (number of shifts N, oil filling time t 1 ) in the high-pressure system.
  • the values of p min and p max are more accurate, and the value range between p min and p max is larger, so that the adjustable range of the pressure value of the main oil circuit 10 is larger and more accurate, so that the electric oil pump 3
  • the frequency of starting is low, and while meeting the functional requirements of the high-pressure system, the pressure range of the main oil circuit 10 of the high-pressure system can be adjusted in real time, and the hydraulic oil supplied on demand can be precisely controlled, so that the overall working efficiency of the automatic transmission is high; and p max selects the smaller value of p max1 and p max2 , and comprehensively considers the requirements on the number of actions of the clutch actuator and the shift actuator in the hydraulic system design index, which can prevent the electric oil pump 3 from running in the limit power area, which may lead to electric The temperature of the oil pump 3 rises rapidly, and it is easy to damage the electric oil pump 3 when running for a long time.

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Abstract

一种自动变速器高压系统的压力控制方法，自动变速器高压系统的压力控制方法包括：确定自动变速器高压系统中的主油路的压力下限值p min：p min＝p(T)+Δp(T)；确定主油路的压力上限值p max：p max＝Min{p max1，p max2}，其中，p max2＝p(T)+Δp N(T，N)；压力传感器（6）将检测到的液压油温度值T下的主油路（10）的压力值p 0传至控制模块后，控制模块根据p 0与p min及p max之间的关系，控制电动油泵（3）的停止或运转以实现主油路的压力的控制。

Description

自动变速器高压系统的压力控制方法
本申请要求申请日为2020年7月22日、申请号为202010712584.0的中国专利申请的优先权，该申请的全部内容通过引用结合在本申请中。
技术领域
本申请涉及变速器技术领域，例如涉及一种自动变速器高压系统的压力控制方法。
背景技术
随着汽车排放越来越严格的法规要求，对自动变速器的工作效率提出了更为严格的要求。对于液压控制的自动变速器来说，采用高低压系统分体结构，其中的低压系统用作冷却润滑，高压系统用于离合器及换挡、驻车机构的控制，并且采用电动油泵对高低压系统进行按需供液压油，以有效提高自动变速器的工作效率。
对于自动变速器中的高压系统来说，高压系统的主油路的压力范围的合理设定是满足自动变速器的高压系统的功能实现及效率提升的关键因素。相关技术中，高压系统通过在主油路中设置蓄能器以进行储蓄压力值，再通过控制电动油泵的开启或关闭，以使主油路的压力值始终保持在主油路的压力上限值及压力下限值范围内，以保证离合器执行机构或者换挡执行机构的动作需求，以满足高压系统的功能要求，且不需要使电动油泵一直处于工作运转状态。
但高压系统中的压力上限值及压力下限值分别采用固定值，由于主油路的压力值受温度、油液量等多种因素的影响较多，在满足各种因素的条件下很容易导致固定压力上限值及固定的压力下限值之间的压力范围较小，使主油路的压力值的可调节范围较小，从而导致电动油泵启动的频率较高，不能根据实际 需求控制压力调节范围，不利于自动变速器总体工作效率的提升。
发明内容
本申请提出了一种自动变速器高压系统的压力控制方法，能够对高压系统的主油路的压力范围进行实时调节，使高压系统的工作效率较高。
一种自动变速器高压系统的压力控制方法，包括：
确定自动变速器高压系统中的主油路的压力下限值p min：p min＝p(T)+Δp(T)，
其中，p(T)为不同温度下的蓄能器的预充气压力，T为温度，
Δp(T)＝Max{Δp 1(T)，Δp 2(T)}，Δp(T)为不同温度下所述主油路需增加的压力值，Δp 1(T)为在p(T)下，离合器执行机构执行一次动作所述主油路需增加的高压液压油的压力值，Δp 2(T)为在p(T)下，换挡执行机构执行一次动作所述主油路需增加的高压液压油的压力值；
确定所述主油路的压力上限值p max：p max＝Min{p max1，p max2}，
其中，
Figure PCTCN2021107859-appb-000001
P out-max为驱动电动油泵3的电机的最大输出功率，单位为W，q为所述电动油泵的排量，单位为mL/rev，ω max为所述电动油泵的最大转速，单位为rev/min，η(T,ω max,p)为最大转速下的所述电动油泵的总效率，p为所述电动油泵的背压，单位为Mpa；
p max2＝p(T)+Δp N(T,N)，N为所述离合器执行机构或者所述换挡执行机构动作的次数，Δp N(T,N)为不同温度下最大的动作次数下的所述主油路需增加的压力值，温度传感器检测液压油的温度值T并传至控制模块，所述控制模块根据温度值T和所述离合器执行机构或者所述换挡执行机构动作的次数N计算出所述下限值p min和所述上限值p max；及
压力传感器将检测到的液压油温度值T下的所述主油路的压力值p 0传至所述控制模块后，所述控制模块根据p 0与p min及p max之间的关系，控制所述电动油泵的停止或运转以实现所述主油路的压力的控制。
在一实施例中，所述控制模块根据p 0与p min及p max之间的关系，控制所述电动油泵的停止或者运转包括：
当p 0>p min时，所述电动油泵不运转；及
当p 0≤p min，所述控制模块控制所述电动油泵开始运转，直至p 0≥p max时，所述控制模块控制所述电动油泵停止运转。
在一实施例中，在所述确定所述主油路的压力上限值p max的步骤中：所述电动油泵输出的液压功率P 1为：
Figure PCTCN2021107859-appb-000002
P out为驱动电动油泵3的电机的输出功率，(单位：W)，ω为电动油泵3的转速(单位：rev/min)，(1)式进行换算，能够得到：
Figure PCTCN2021107859-appb-000003
且使所述电动油泵的转速ω的值为最大，即
ω＝ω max           (3)
将(3)式带入(2)式，以得到p max1：
Figure PCTCN2021107859-appb-000004
其中，忽略所述高压系统中的用于过滤液压油的过滤器的压降。
在一实施例中，在所述控制模块控制所述电动油泵的步骤中：所述控制模块控制所述电动油泵运转的转速为
Figure PCTCN2021107859-appb-000005
其中，t 1为所述电动油泵运转时，使所述主油路上的压力值从0到预先设定的标定测试压力值所需要的时间；ω max(T)为不同温度下满足NVH性能要求的所述电动油泵的最大转速，ω min(T,t 1)为0-t 1时间内，不同温度T下电动泵转速 下限。
在一实施例中，p(T)、Δp 1(T)，Δp 2(T)均通过试验获得。
在一实施例中，所述电动油泵的总效率η(T,ω max,p)包括所述电动油泵在最大转速下的机械效率和容积效率，η(T,ω max,p)通过查询表格获得。
在一实施例中，Δp N(T,N)通过查询表格获得。
在一实施例中，所述电动油泵的转速ω min(T,t 1)及转速ω max(T)均通过试验获得。
在一实施例中，所述高压系统包括电控开关阀，所述控制模块根据p 0与p min及p max之间的关系，控制所述电动油泵的停止或者运转包括：所述控制模块可以通过控制所述高压系统中的电控开关阀，以断开所述主油路或者连通所述主油路，以控制所述电动油泵的停止或者运转。
附图说明
图1是本申请实施例一提供的自动变速器高压系统的结构示意图；
图2是本申请实施例二提供的自动变速器高压系统的压力控制方法的流程示意图；
图3是一实施例提供的动变速器高压系统的压力控制方法的流程示意图。
附图标记说明：
1-油箱；2-温度传感器；3-电动油泵；4-过滤器；5-单向阀；6-压力传感器；7-蓄能器；8-离合器控制油路；9-换挡控制油路；10-主油路。
具体实施方式
实施例一
本实施例中，提出了一种自动变速器高压系统，自动变速器高压系统用于 离合器及换挡、驻车机构的控制，以分别为离合器控制油路8和换挡控制油路9提供高压液压油，以满足离合器及换挡的功能需求。
在一实施例中，如图1所示，自动变速器高压系统包括依次设置在主油路10上的用于存放液压油的油箱1、电动油泵3、过滤器4及蓄能器7。其中，蓄能器7分别与离合器控制油路8及换挡控制油路9连接，蓄能器7设置为将主油路10中的压力转变为压缩能储存起来，当主油路10需要压力时，蓄能器7能够将压缩能转变为压力能释放出来，以重新补供给离合器控制油路8或换挡控制油路9。通过设置蓄能器7能够储存部分压力以供给离合器控制油路8或换挡控制油路9，以避免电动油泵3持续不断地工作。过滤器4设置为过滤油箱1中经电动油泵3泵出的液压油中的杂质，且在过滤器4与蓄能器7之间设置有单向阀5，以防止主油路10中的液压油回流至油箱1内；在单向阀5与蓄能器7之间设置有压力传感器6，以实时监测高压系统中的主油路10的压力值p 0，在油箱1内设置有温度传感器2，以实时检测油箱1内液压油的温度T。
在一实施例中，自动变速器高压系统还包括控制模块(图中未示出)，控制模块分别与温度传感器2、压力传感器6及电动油泵3控制连接；控制模块设置为接收温度传感器2检测的温度值及压力传感器6的压力值，并根据温度值及压力值控制电动油泵3的运转或停止。本实施例中的控制模块为相关技术中的常用控制模块，因此，此处不再对控制模块的具体结构及工作原理进行详细赘述。本实施例中，电动油泵3为单泵。其它实施例中，电动油泵3还可以为双联泵。
实施例二
本实施例提出了一种实施例一中的自动变速器高压系统的压力控制方法，能够实时控制高压系统中的主油路10上的压力上限值p max及压力下限值p min， 使控制范围较大且较为精准。
自动变速器高压系统的压力控制方法，如图2和图3所示，包括以下步骤：
S1中，确定自动变速器高压系统中的主油路10的压力下限值p min：p min＝p(T)+Δp(T)；
其中，p(T)为不同温度下的蓄能器7的预充气压力，T为温度，p(T)为蓄能器7的自身特性，p(T)的具体关系式能够通过试验获得；
Δp(T)＝Max{Δp 1(T)，Δp 2(T)}，即Δp(T)取值为Δp 1(T)及Δp 2(T)两者中数值较大的一个，Δp(T)为不同温度下主油路10需增加的压力值，Δp 1(T)为在p(T)下，离合器执行机构执行一次动作，主油路10需增加的高压液压油的压力值，Δp 2(T)为在p(T)下，换挡执行机构执行一次动作，主油路10需增加的高压液压油的压力值。
Δp(T)取值为Δp 1(T)及Δp 2(T)两者中数值较大的一个，能够保证主油路10的压力处于最低时，若离合器执行机构或换挡执行机构有动作需求，蓄能器7的储蓄量能够至少保证维持离合器执行机构或换挡执行机构一次动作，以给电动油泵3进行重新启动的时间余量。其中，Δp 1(T)及Δp 2(T)的具体关系式均能够通过试验获得。
S2中，确定主油路10的压力上限值p max：p max＝Min{p max1，p max2}，
其中，
Figure PCTCN2021107859-appb-000006
P out-max为驱动电动油泵3的电机的最大输出功率，单位为W，为已知定值，q为电动油泵3的排量，单位为mL/rev，为已知定值，ω max为电动油泵3的最大转速，单位为rev/min，η(T,ω max,p)为最大转速下的电动油泵3的总效率，p为电动油泵3的背压，单位为兆帕(Mpa)；其中，电动油泵3的总效率η(T,ω max,p)包括电动油泵3在最大转速下的机械效率和容积效率，η(T,ω max,p)能够通过试验获得关于η(T,ω max,p)分别与T,ω及p 之间的关系表格，通过查询试验得出的关系表格获得在当前温度T及ω＝ω max下的η(T,ω max,p)，从而得出p max1的具体数值。
p max2＝p(T)+Δp N(T,N)，N为离合器执行机构或者换挡执行机构动作的次数，Δp N(T,N)为不同温度下最大的动作次数下的主油路10需增加的压力值；Δp N(T,N)能够通过试验获得关于Δp N(T,N)分别与T及N之间的关系表格，通过查询试验得出的关系表格获得在当前温度T及N下的Δp N(T,N)，且p(T)的具体关系式能够通过试验获得，从而得出p max2的具体数值。
其中，在确定主油路10的压力上限值p max的步骤中：电动油泵3输出的液压功率P 1为：
Figure PCTCN2021107859-appb-000007
P out为驱动电动油泵3的电机的输出功率，(单位：W)，ω为电动油泵3的转速(单位：rev/min)，对(1)式进行换算，能够得到：
Figure PCTCN2021107859-appb-000008
且使电动油泵的转速ω的值为最大，即
ω＝ω max          (3)
将(3)式带入(2)式，以得到p max1：
Figure PCTCN2021107859-appb-000009
其中，忽略高压系统中用于过滤高压油的过滤器4的压降。
在一实施例中，自动变速器高压系统的压力控制方法还包括以下步骤：
S3中，压力传感器6将检测到的液压油温度值T下的所述主油路10的压力值p 0传至所述控制模块后，所述控制模块根据p 0与p min及p max之间的关系，控制所述电动油泵3的停止或运转以实现主油路的压力的控制。
首先，确定出离合器执行机构或者换挡执行机构动作的次数N，将p min＝p(T)+Δp(T)及p max＝Min{p max1，p max2}中的每个关系式及关系表格 分别输入至控制模块内；然后，温度传感器2将检测的实时的液压油的温度T传至控制模块，控制模块根据接收到的温度值T及预先确定的离合器执行机构或者换挡执行机构动作的次数N分别计算出p min及p max的具体数值；最后，压力传感器6将检测到的此温度T下的主油路10的压力值p 0传至控制模块，控制模块根据接收到的p 0与计算得出的p min及p max之间的关系，以控制电动油泵3的停止或者运转，从而实现对主油路的压力的控制。
通过计算得出自动变速器的高压系统中的主油路10的压力下限值为p min＝p(T)+Δp(T)，Δp(T)＝Max{Δp 1(T)，Δp 2(T)}，以及高压系统中的主油路10的压力上限值为p max＝Min{p max1，p max2}，
Figure PCTCN2021107859-appb-000010
p max2＝p(T)+Δp N(T,N)，使主油路10的p min及p max能够根据实时的液压油的温度以及离合器执行机构或者换挡执行机构动作的次数实时计算得出，使p min及p max的数值更为精准，p min及p max之间的数值范围更大，以使主油路10的压力值的可调节范围较大且精准，从而使电动油泵3启动的频率较低，在满足高压系统的功能要求的同时，能够对高压系统的主油路10的压力范围进行实时调节，精准控制按需供给液压油，使自动变速器总体工作效率较高；且p max选取p max1与p max2中的较小值，综合考虑了液压系统设计指标中对离合器执行机构及换挡执行机构动作次数的要求，能够避免电动油泵3运行在极限功率区，而导致电动油泵3的温度升高较快，长时间运行易损坏电动油泵3的问题。
其中，如图2所示，在S3中：
当p 0>p min时，控制模块控制电动油泵3不运转，即此时主油路10的压力值能够维持离合器执行机构或换挡执行机构至少一次动作，暂时不需要电动油泵3供给高压油。
当p 0≤p min，即此时主油路10的压力值不能够维持离合器执行机构或换挡执行机构一次动作，控制模块控制电动油泵3开始运转，以对主油路10进行持续供给高压油，以满足离合器执行机构或换挡执行机构的性能需求；直至电动油泵3供油至p 0≥p max时，即此时主油路10的压力足以维持离合器执行机构或换挡执行机构的性能需求，且避免电动油泵3在极限功率区进行运转以损坏电动油泵3的问题，控制模块控制电动油泵3停止运转。本实施例中，直接通过控制模块与电动油泵3进行控制连接，以控制电动油泵3的停止或者运转。其它实施例中，还可以在主油路10上的过滤器4与单向阀5之间设置电控开关阀，使控制模块与电控开关阀控制连接，以使控制模块控制电控开关阀的开闭，从而实现对电动油泵3的运转或停止。具体的控制方式需要根据实际的工作需求及工况决定。
在一实施例中，由于电动油泵3转速越快，则充油速度越快，充油时间越短，但随着电动油泵3转速的增大，高压系统的噪声、振动与声振粗糙度(Noise,Vibration,Harshness，NVH)性能会发生恶化，且电动油泵3的转速受温度影响较大。为了使电动油泵3的转速能够满足转动需求及温度、NVH性能要求，在S3中：控制模块控制电动油泵3运转时的转速为
Figure PCTCN2021107859-appb-000011
其中，t 1为电动油泵3运转时，使主油路10上的压力值从0到预先设定的标定测试压力值所需要的时间，t 1能够通过试验获得。
ω max(T)为不同温度下满足NVH性能要求的电动油泵3的最大转速，ω max(T)能够通过试验获得。其中，NVH性能是最直接和最表面衡量汽车制造质量的一个综合性因素，ω min(T,t 1)为0-t 1时间内，不同温度T下电动泵转速下限。
本实施例中的自动变速器高压系统的压力控制方法的具体控制过程如下： 如图2所示，首先，电动油泵3停止运转，即此时ω＝0，将p min＝p(T)+Δp(T)、p max＝Min{p max1，p max2}及
Figure PCTCN2021107859-appb-000012
中的已知数值、关系式及关系表格分别输入至控制模块内，并确定出离合器执行机构或者换挡执行机构动作的次数N并传至控制模块内。
然后，温度传感器2将检测的实时的液压油的温度T传至控制模块，控制模块根据接收到的温度值T及预先确定的已知数值分别计算出此温度下的p min、p max及ω的具体数值；且压力传感器6将检测到的此温度T下的主油路10的压力值p 0传至控制模块，控制模块接收p 0。
最后，控制模块根据接收到的p 0与计算得出的p min及p max之间的关系，以控制电动油泵3的停止或者运转；在一实施例中，当控制模块判断出p 0>p min时，电动油泵3不运转ω＝0，即此时主油路10的压力值能够维持离合器执行机构或换挡执行机构至少一次动作，暂时不需要电动油泵3供给高压油；当控制模块判断出p 0≤p min时，即此时主油路10的压力值不能够维持离合器执行机构或换挡执行机构一次动作，控制模块控制电动油泵3开始以
Figure PCTCN2021107859-appb-000013
的运转速度进行运转，以对主油路10进行持续供给高压油，以满足离合器执行机构或换挡执行机构的性能需求；直至当控制模块判断出p 0≥p max时，即此时主油路10的压力足以维持离合器执行机构或换挡执行机构的性能需求，且避免电动油泵3在极限功率区进行运转以损坏电动油泵3的问题，控制模块控制电动油泵3停止运转，即，ω＝0。
其中，由于存在泄漏以及离合器执行机构或换挡执行机构动作会持续消耗液压油，即主油路10的压力p 0≥p max持续一段时间后，控制模块会根据实时的温度T计算并判断出p 0≤p min；当控制模块再次计算并判断得出p 0≤p min时，重复上述控制过程，以实现对自动变速器高压系统中的主油路10的压力的控制。 其中，p min、p max及ω与高压系统中的实时油温T、控制要求(换挡次数N、充油时间t 1)的变化而实时改变。
通过计算得出自动变速器的高压系统中的主油路10的压力下限值为p min＝p(T)+Δp(T)，Δp(T)＝Max{Δp 1(T)，Δp 2(T)}，以及高压系统中的主油路10的压力上限值为p max＝Min{p max1，p max2}，
Figure PCTCN2021107859-appb-000014
p max2＝p(T)+Δp N(T,N)，使主油路10的p min及p max能够根据实时的液压油的温度以及离合器执行机构或者换挡执行机构动作的次数实时计算得出，使p min及p max的数值更为精准，p min及p max之间的数值范围更大，以使主油路10的压力值的可调节范围较大且精准，从而使电动油泵3启动的频率较低，在满足高压系统的功能要求的同时，能够对高压系统的主油路10的压力范围进行实时调节，精准控制按需供给液压油，使自动变速器总体工作效率较高；且p max选取p max1与p max2中的较小值，综合考虑了液压系统设计指标中对离合器执行机构及换挡执行机构动作次数的要求，能够避免电动油泵3运行在极限功率区，而导致电动油泵3的温度升高较快，长时间运行易损坏电动油泵3的问题。

Claims (9)

  1. 一种自动变速器高压系统的压力控制方法，包括：
    确定自动变速器高压系统中的主油路(10)的压力下限值p min：p min＝p(T)+Δp(T)，
    其中，p(T)为不同温度下的蓄能器(7)的预充气压力，T为温度，
    Δp(T)＝Max{Δp 1(T)，Δp 2(T)}，Δp(T)为不同温度下所述主油路(10)需增加的压力值，Δp 1(T)为在p(T)下，离合器执行机构执行一次动作所述主油路(10)需增加的高压液压油的压力值，Δp 2(T)为在p(T)下，换挡执行机构执行一次动作所述主油路(10)需增加的高压液压油的压力值；
    确定所述主油路(10)的压力上限值p max，p max＝Min{p max1，p max2}，
    其中，
    Figure PCTCN2021107859-appb-100001
    P out-max为驱动电动油泵(3)的电机的最大输出功率，单位为W，q为所述电动油泵(3)的排量，单位为mL/rev，ω max为所述电动油泵(3)的最大转速，单位为rev/min，η(T,ω max,p)为最大转速下的所述电动油泵(3)的总效率，p为所述电动油泵(3)的背压，单位为Mpa；
    p max2＝p(T)+Δp N(T,N)，N为所述离合器执行机构或者所述换挡执行机构动作的次数，Δp N(T,N)为不同温度下最大的动作次数下的所述主油路(10)需增加的压力值，温度传感器(2)检测液压油的温度值T并传至控制模块，所述控制模块根据温度值T和所述离合器执行机构或者所述换挡执行机构动作的次数N计算出所述下限值p min和所述上限值p max；及
    压力传感器(6)将检测到的液压油温度值T下的所述主油路(10)的压力值p 0传至所述控制模块后，所述控制模块根据p 0与p min及p max之间的关系，控制所述电动油泵(3)的停止或运转以实现所述主油路(10)的压力的控制。
  2. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，所述控 制模块根据p 0与p min及p max之间的关系，控制所述电动油泵(3)的停止或者运转包括：
    当p 0>p min时，所述电动油泵(3)不运转；
    当p 0≤p min，所述控制模块控制所述电动油泵(3)开始运转，直至p 0≥p max时，所述控制模块控制所述电动油泵(3)停止运转。
  3. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，在所述确定所述主油路(10)的压力上限值p max中：所述电动油泵(3)输出的液压功率P 1为：
    Figure PCTCN2021107859-appb-100002
    P out为驱动电动油泵3的电机的输出功率，(单位：W)，ω为电动油泵的转速(单位：rev/min)，对(1)式进行换算，能够得到：
    Figure PCTCN2021107859-appb-100003
    且使所述电动油泵的转速ω的值为最大，即
    ω＝ω max      (3)
    将(3)式带入(2)式，以得到
    Figure PCTCN2021107859-appb-100004
    其中，忽略所述高压系统中的用于过滤液压油的过滤器(4)的压降。
  4. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，所述电动油泵(3)运转的转速为
    Figure PCTCN2021107859-appb-100005
    其中，t 1为所述电动油泵(3)运转时，使所述主油路(10)上的压力值从0到预先设定的标定测试压力值所需要的时间，
    ω max(T)为不同温度下满足NVH性能要求的所述电动油泵(3)的最大转速，ω min(T,t 1)为0-t 1时间内，不同温度T下电动泵转速下限。
  5. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，p(T)、 Δp 1(T)，Δp 2(T)通过试验获得。
  6. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，所述电动油泵(3)的总效率η(T,ω max,p)包括所述电动油泵(3)在最大转速下的机械效率和容积效率，η(T,ω max,p)通过查询表格获得。
  7. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，Δp N(T,N)通过查询表格获得。
  8. 如权利要求4所述的自动变速器高压系统的压力控制方法，其中，所述电动油泵(3)的转速ω min(T,t 1)及转速ω max(T)通过试验获得。
  9. 如权利要求1所述的自动变速器高压系统的压力控制方法，其中，所述高压系统包括电控开关阀；
    所述控制模块根据p 0与p min及p max之间的关系，控制所述电动油泵(3)的停止或者运转包括所述控制模块通过控制所述电控开关阀，断开所述主油路(10)或者连通所述主油路(10)，以控制所述电动油泵(3)的停止或者运转。
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