CN112984090A - Control method of duplex pump for transmission - Google Patents
Control method of duplex pump for transmission Download PDFInfo
- Publication number
- CN112984090A CN112984090A CN202110221050.2A CN202110221050A CN112984090A CN 112984090 A CN112984090 A CN 112984090A CN 202110221050 A CN202110221050 A CN 202110221050A CN 112984090 A CN112984090 A CN 112984090A
- Authority
- CN
- China
- Prior art keywords
- pressure
- hydraulic pump
- low
- pressure hydraulic
- demand
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0436—Pumps
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
Abstract
The invention belongs to the technical field of transmissions, and discloses a control method of a duplex pump for a transmission, which comprises the steps of S100, determining the output flow Q of a high-pressure hydraulic pump1About oil temperature T, rotating speed n of external power source, outlet pressure p of high-pressure hydraulic pump1First functional relationship f1And output flow rate Q of low-pressure hydraulic pump2About oil temperature T, rotation speed n of external power source, outlet pressure p of low-pressure hydraulic pump2Second functional relationship of f2(ii) a S200, according to the first functional relation f1Is inverse function f1 ‑1Determining the attainment of a high pressure demand flow QR1High pressure demand speed n of high pressure hydraulic pump1According to the inverse function f of the second functional relationship2 ‑2Determining the attainment of a low pressure demand flow QR2Low pressure demand speed n of low pressure hydraulic pump2And a target rotational speed N of the external power source is obtained. The final target rotating speed can be determined by obtaining the function relation which is inverse function of the output flow, the oil temperature, the rotating speed of the power source and the outlet pressure of the hydraulic pump,the problem of two hydraulic pumps coupled in cooperation is solved.
Description
Technical Field
The invention relates to the technical field of transmissions, in particular to a control method of a duplex pump for a transmission.
Background
With the increasing living standard of people, more and more automobiles enter each family, and people also put higher requirements on the comfort of the automobiles. Automobiles equipped with automatic transmissions are becoming more and more popular because of their ease of operation, and their market share has increased year by year, and they have become mainstream arrangements in the market.
The hydraulic pump is a power source of a hydraulic system of the automatic transmission of the automobile and provides lubricating oil with sufficient pressure and flow rate for the hydraulic system. The pressure oil is pumped from an oil pan by a hydraulic pump, is pressurized by the hydraulic pump to enter a hydraulic system, and drives an actuating element and lubricates and cools various moving parts after the pressure and flow of each stage of hydraulic valve are controlled.
In recent years, in order to improve the driving efficiency, a novel hydraulic pump appears on a transmission, which is different from a traditional hydraulic pump, the traditional hydraulic pump usually drives one hydraulic pump by one external power source (an engine or a motor), and the hydraulic pump supplies oil to a high-pressure oil way and a low-pressure oil way of a hydraulic system respectively by one external power source (the engine or the motor) through coaxially driving two hydraulic pumps, and simultaneously outputs two kinds of pressure and flow, so that the situation that the traditional hydraulic pump can only output one kind of pressure/flow to the hydraulic system at the same time is avoided, and the energy loss is caused by the internal pressure reduction of the hydraulic system, thereby improving the system efficiency.
The same external power source drives two hydraulic pumps simultaneously, which causes the problem that the two hydraulic pumps work cooperatively to generate coupling, so a good control method needs to be established to eliminate the coupling problem.
Disclosure of Invention
The invention aims to provide a control method of a duplex pump for a transmission, which aims to solve the problem that two hydraulic pumps are coupled when working cooperatively.
In order to achieve the purpose, the invention adopts the following technical scheme:
a method of dual pump control for a transmission, comprising:
s100, determining output flow Q of high-pressure hydraulic pump1About oil temperature T, rotating speed n of external power source, outlet pressure p of high-pressure hydraulic pump1First functional relationship f1And output flow rate Q of low-pressure hydraulic pump2About oil temperature T, rotation speed n of external power source, outlet pressure p of low-pressure hydraulic pump2Second functional relationship of f2；
S200, according to the first functional relation f1Is inverse function f1 -1Determining the attainment of a high pressure demand flow QR1High pressure demand speed n of high pressure hydraulic pump1According to the inverse function f of the second functional relationship2 -2Determining the attainment of a low pressure demand flow QR2Low pressure demand speed n of low pressure hydraulic pump2And a target rotational speed N of the external power source is obtained.
As a preferable mode of the twin pump control method for a transmission, the high pressure demand flow rate Q isR1And the output flow rate Q of the high-pressure hydraulic pump1Should satisfy:
Q1≥QR1；
the low pressure demand flow rate QR2And the output flow rate Q of the low-pressure hydraulic pump2Should satisfy:
Q2≥QR2。
as a preferable aspect of the above-described twin pump control method for a transmission, the target rotation speed N and the high pressure required rotation speed N are1And the low pressure required rotation speed n2The relationship of (1) is:
N＝max{n1,n2}。
as a preferable aspect of the above-described method for controlling a twin pump for a transmission, the method further includes, after step S200:
s300, determining the target rotating speed N according to the working condition and the pressure of the high-pressure oil way.
As a preferable scheme of the twin pump control method for the transmission, in step S301, when the operating condition is that the pressure of the high-pressure oil line is lower than the lower limit value and continuous gear shifting is required, the target rotation speed N is the maximum design rotation speed.
As a preferable aspect of the above-described method for controlling a twin pump for a transmission, the step S300 further includes:
s302, when the working condition is that the pressure of the high-pressure oil way is lower than the lower limit value and continuous gear shifting is not needed, the high-pressure oil way needs to be increased to the upper limit value so as to obtain the output flow Q of the low-pressure hydraulic pump2For the control target, the output flow Q of the low-pressure hydraulic pump2Is the sum of the flow demand for clutch lubrication and the flow demand for shaft tooth lubrication.
As a preferable aspect of the above-described method for controlling a twin pump for a transmission, the step S300 includes:
s303, when the working condition is that the pressure of the high-pressure oil way is between an upper limit value and a lower limit value and the high-pressure oil way does not need to be supplemented by hydraulic oil, the output flow Q of the low-pressure hydraulic pump is used2For the control target, the output flow Q of the low-pressure hydraulic pump2And simultaneously closing the outlet end of the high-pressure hydraulic pump for the sum of the flow demand of the clutch lubrication and the flow demand of the shaft tooth lubrication.
As a preferable aspect of the above-described method for controlling a twin pump for a transmission, the step S300 includes:
and S304, when the working condition is shutdown, closing the high-pressure hydraulic pump and the low-pressure hydraulic pump.
As a preferable aspect of the above-described method for controlling a twin pump for a transmission, the step S300 includes:
s305, when the working condition is that the low-pressure oil way needs the maximum lubricating flow, the pressure of the high-pressure oil way is lower than the lower limit value, andwhen the pressure does not need to be increased urgently, the output flow Q of the low-pressure hydraulic pump is used2For the control target, the target rotating speed N is the corresponding low-pressure required rotating speed N when the maximum output flow of the low-pressure hydraulic pump can be achieved under the oil temperature and the outlet pressure2。
The invention has the beneficial effects that: the function relation which is inverse functions of the output flow, the oil temperature, the power source rotating speed and the outlet pressure of the hydraulic pump is obtained, the final target rotating speed can be determined, and the problem that the two hydraulic pumps are coupled in cooperative work is solved.
Drawings
FIG. 1 is a schematic view of a dual pump system for a transmission according to an embodiment of the present disclosure.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some of the structures related to the present invention are shown in the drawings, not all of the structures.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
In the description of the present embodiment, the terms "upper", "lower", "right", etc. are used in an orientation or positional relationship based on that shown in the drawings only for convenience of description and simplicity of operation, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used only for descriptive purposes and are not intended to have a special meaning.
The invention provides a control method of a duplex pump for a transmission, which is used in the duplex pump system for the transmission shown in figure 1.
The duplex pump control system for the transmission comprises an oil tank 1, a high-pressure oil path and a low-pressure oil path.
The high-pressure oil way comprises a high-pressure hydraulic pump 2, a high-pressure oil way pressure control valve 3, a one-way valve 4, a pressure sensor 5, an energy accumulator 6 and a high-pressure load 7, the input end of the high-pressure hydraulic pump 2 is connected with the oil tank 1, the output end of the high-pressure hydraulic pump 2 is connected with the high-pressure oil way pressure control valve 3 and the one-way valve 4 in parallel, the output end of the one-way valve 4 is connected to the energy accumulator 6 and the high-pressure load 7 in parallel, the pressure sensor 5 is arranged between the output end of the one-way valve 4 and the input end of the energy accumulator 6, and the output end of.
The low pressure oil circuit includes low pressure hydraulic pump 8, the lubricated valve of axle teeth 9 and the lubricated valve of clutch 10, and oil tank 1 is connected to low pressure hydraulic pump 8's input, and the output of low pressure hydraulic pump 8 is parallelly connected to the lubricated valve of axle teeth 9 and the lubricated valve of clutch 10, and low pressure hydraulic pump 8 and the output shaft of the coaxial coupling of high pressure hydraulic pump 2 to external power source 11.
Preferably, the outlet end of the low-pressure hydraulic pump 8 is also provided with a cooler 12, and the oil passes through the cooler 12 and then enters the shaft tooth lubricating valve 9 and the clutch lubricating valve 10 in parallel.
It should be noted that, when the pressure of the high-pressure oil line measured by the pressure sensor 5 is lower than the lower limit value, the high-pressure oil line pressure control valve 3 is closed, and at this time, the oil does not flow back to the oil tank 1 through the high-pressure oil line pressure control valve 3. When the pressure sensor 5 detects that the pressure of the high-pressure oil circuit is higher than the upper limit value, the high-pressure oil circuit pressure control valve 3 is opened.
The high-pressure hydraulic pump 2 is used for supplying oil to a high-pressure oil path and is characterized by small displacement and high output pressure. The low-pressure hydraulic pump 8 is used for supplying oil to a low-pressure oil path, and is characterized in that the displacement is large, the output pressure is low, and the high-pressure hydraulic pump 2 and the low-pressure hydraulic pump 8 have the same rotating speed.
The duplex pump control method for the transmission comprises the following steps: s100, determining the output flow Q of the high-pressure hydraulic pump 21Regarding the oil temperature T, the rotational speed n of the external power source 11, and the outlet pressure p of the high-pressure hydraulic pump 21First functional relationship f1And the output flow rate Q of the low-pressure hydraulic pump 82With respect to the oil temperature T, the rotational speed n of the external power source 11, and the low-pressure hydraulic pump outlet pressure p2Second functional relationship of f2。
Due to the output flow Q of the high-pressure hydraulic pump 21And the output flow rate Q of the low-pressure hydraulic pump 82Are all related to the rotational speed of the output shaft of the external power source 11, and thus output flow rate Q1And output flow rate Q2The method has a certain coupling relation, and the relation is determined by testing the output flow of the two pumps at a certain oil temperature T and a certain rotating speed n:
Q1＝f1(T,n,p1)，Q2＝f2(T,n,p2)。
s200, according to the first functional relation f1Is inverse function f1 -1Determining the attainment of a high pressure demand flow QR1High pressure demand speed n of the high pressure hydraulic pump 21According to the inverse function f of the second functional relationship2 -2Determining the attainment of a low pressure demand flow QR2Low pressure demand speed n of low pressure hydraulic pump 82And the target rotation speed N of the external power source 11 is obtained.
It should be noted that the high pressure demand flow rate QR1And the output flow rate Q of the high-pressure hydraulic pump 21Should satisfy Q1≥QR1. Low pressure demand flow QR2And the output flow rate Q of the low-pressure hydraulic pump 82Should satisfy Q2≥QR2。
Thus, the output flow rate Q1Of the high-pressure hydraulic pump 21And output flow rate Q2Of the low-pressure hydraulic pump 82Respectively as follows:
n1＝f1 -1(T,p1,Q1)，n2＝f2 -1(T,p2,Q2)。
target speed N and high pressure demand speed N1And low pressure demand speed n2The relationship of (1) is: n ═ max { N ═ N1,n2}. I.e. the target speed is the high pressure demand speed n1And low pressure demand speed n2The larger value, thereby satisfying the demands of the high-pressure hydraulic pump 2 and the low-pressure hydraulic pump 8 at the same time.
Further, the output flows of the high-pressure hydraulic pump 2 and the low-pressure hydraulic pump 8 may be determined according to the design condition of the transmission.
Generally, the working conditions of the high-pressure oil circuit comprise three types, namely that the high-pressure oil circuit urgently needs oil supply, the high-pressure oil circuit generally supplies oil and the high-pressure oil circuit stops supplying oil. The working condition of the low-pressure oil way comprises that the low-pressure oil way supplies oil as required, the low-pressure oil way stops supplying oil and the low-pressure oil way supplies the oil maximally.
And the low-pressure oil circuit working condition and the high-pressure oil circuit working condition are combined, and the target rotating speed N is determined according to the working conditions and the pressure of the high-pressure oil circuit.
Working condition 1: the high-pressure oil way supplies oil quickly and the low-pressure oil way supplies oil as required.
Specifically, the working condition 1 is: when the pressure of the high-pressure oil line is lower than the lower limit value and continuous gear shifting is needed (such as continuous quick downshift), the pressure of the high-pressure oil line is needed to be increased to the maximum limit value rapidly. At this time, the target rotating speed N is the highest designed rotating speed of the external power source 11, the low-pressure hydraulic pump 8 passively outputs the maximum flow, the clutch lubrication valve 10 in the low-pressure oil path is controlled to have the maximum opening, the lubricating oil flow resistance of the high-pressure oil path is reduced as much as possible, and the power consumption of the hydraulic duplex pump is reduced.
Working condition 2: the high-pressure oil circuit generally supplies oil and the low-pressure oil circuit supplies oil as required.
Specifically, when the hydraulic system pressure is lower than the lower limit value and continuous gear shifting is not required, the high-pressure oil circuit needs to be supplemented with hydraulic oil to increase the system pressure to the upper limit value under the working condition 2. The low-pressure hydraulic pump 8 outputs the flow Q at the moment2Is the control target. Output flow Q of low-pressure hydraulic pump 82The sum of the flow required by the clutch lubrication and the flow required by the shaft tooth lubrication is used as the method for controlling the rotating speed of the hydraulic pump, so that the low-pressure hydraulic pump 8 outputs the flow Q2Greater than low pressure demand flow QR2。
Working condition 3: the high-pressure oil way stops supplying oil and the low-pressure oil way supplies oil as required.
Specifically, the working condition 3 is that the pressure of the hydraulic system is between a lower limit value and an upper limit value, the high-pressure oil path does not need to be supplemented by hydraulic oil, and the low-pressure hydraulic pump 8 outputs the flow Q at the moment2Is the control target. Output flow Q of low-pressure hydraulic pump 82The sum of the flow required by the clutch lubrication and the flow required by the shaft tooth lubrication is used as the method for controlling the rotating speed of the hydraulic pump, so that the low-pressure hydraulic pump 8 outputs the flow Q2Greater than low pressure demand flow QR2And the high-pressure hydraulic pump 2 is closed, so that the oil at the outlet of the high-pressure hydraulic pump 2 flows back to the oil tank 1.
Working condition 4: the high-pressure oil circuit stops supplying oil and the low-pressure oil circuit stops supplying oil.
Specifically, condition 4 is a shutdown state. The high-pressure hydraulic pump 2 and the low-pressure hydraulic pump 8 stop operating.
Working condition 5: the high-pressure oil way generally supplies oil and the low-pressure oil way supplies oil to the maximum.
The working condition 5 is that the low-pressure oil circuit needs the maximum lubricating flow, the pressure of the high-pressure oil circuit is lower than the lower limit value, and the high-pressure hydraulic pump 2 is used for supplying oil for the high-pressure system generally without emergency pressure lifting (if continuous gear shifting is needed). The oil supply of the low-pressure oil way is in a maximum oil supply state, the maximum lubrication flow required by the clutch and the shaft gear or the oil temperature reaches an upper limit value, the oil flow needs to be increased in the cooler, and the oil cooling is accelerated.
Under the working condition, the target rotating speed N is the corresponding low-pressure required rotating speed N when the maximum output flow of the low-pressure hydraulic pump 8 can be achieved under the oil temperature and the outlet pressure2From the formula n2＝f2 -1(T,p2,Q2) And (4) determining. Due to the rotating speed coupling relationship of the high-pressure hydraulic pump 2 and the low-pressure hydraulic pump 8, the high-pressure hydraulic pump 2 passively outputs a large flow, and the upper limit of the pressure of the high-pressure hydraulic system is correspondingly adjusted downwards, so that the power consumption of the hydraulic duplex pump is reduced.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Numerous obvious variations, adaptations and substitutions will occur to those skilled in the art without departing from the scope of the invention. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (9)
1. A method of controlling a twin pump for a transmission, comprising:
s100, determining output flow Q of high-pressure hydraulic pump1About oil temperature T, rotating speed n of external power source, outlet pressure p of high-pressure hydraulic pump1First functional relationship f1And output flow rate Q of low-pressure hydraulic pump2About oil temperature T, rotation speed n of external power source, outlet pressure p of low-pressure hydraulic pump2Second functional relationship of f2；
S200, according to the first functional relation f1Is inverse function f1 -1Determining the attainment of a high pressure demand flow QR1High pressure demand speed n of high pressure hydraulic pump1According to the inverse function f of the second functional relationship2 -2Determining the attainment of a low pressure demand flow QR2Low pressure demand speed n of low pressure hydraulic pump2And a target rotational speed N of the external power source is obtained.
2. The twin pump control method for a transmission according to claim 1, wherein the high pressure demand flow rate QR1And the output flow rate Q of the high-pressure hydraulic pump1Should satisfy:
Q1≥QR1；
the low pressure demand flow rate QR2And the output flow rate Q of the low-pressure hydraulic pump2Should satisfy:
Q2≥QR2。
3. the twin pump control method for a transmission according to claim 2, wherein the target rotation speed N and the high pressure demand rotation speed N1And the low pressure required rotation speed n2The relationship of (1) is:
N＝max{n1,n2}。
4. the twin pump control method for a transmission according to any one of claims 1 to 3, further comprising, after step S200:
s300, determining the target rotating speed N according to the working condition and the pressure of the high-pressure oil way.
5. The twin pump control method for a transmission according to claim 4, wherein the step S300 includes:
s301, when the working condition is that the pressure of the high-pressure oil way is lower than a lower limit value and continuous gear shifting is needed, the target rotating speed N is the maximum design rotating speed.
6. The twin pump control method for a transmission according to claim 4, wherein the step S300 further includes:
s302, when the working condition is that the pressure of the high-pressure oil way is lower than the lower limit value and continuous gear shifting is not needed, the high-pressure oil way needs to be increased to the upper limit value so as to obtain the output flow Q of the low-pressure hydraulic pump2For the control target, the output flow Q of the low-pressure hydraulic pump2Flow demand for clutch lubrication and shaft tooth lubrication demandThe sum of the flow rates.
7. The twin pump control method for a transmission according to claim 4, wherein the step S300 includes:
s303, when the working condition is that the pressure of the high-pressure oil way is between an upper limit value and a lower limit value and the high-pressure oil way does not need to be supplemented by hydraulic oil, the output flow Q of the low-pressure hydraulic pump is used2For the control target, the output flow Q of the low-pressure hydraulic pump2And simultaneously closing the outlet end of the high-pressure hydraulic pump for the sum of the flow demand of the clutch lubrication and the flow demand of the shaft tooth lubrication.
8. The twin pump control method for a transmission according to claim 4, wherein the step S300 includes:
and S304, when the working condition is shutdown, closing the high-pressure hydraulic pump and the low-pressure hydraulic pump.
9. The twin pump control method for a transmission according to claim 4, wherein the step S300 includes:
s305, when the working condition is that the low-pressure oil circuit needs the maximum lubricating flow, the pressure of the high-pressure oil circuit is lower than the lower limit value and the emergency pressure rise is not needed, the output flow Q of the low-pressure hydraulic pump is used2For the control target, the target rotating speed N is the corresponding low-pressure required rotating speed N when the maximum output flow of the low-pressure hydraulic pump can be achieved under the oil temperature and the outlet pressure2。
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110221050.2A CN112984090B (en) | 2021-02-26 | 2021-02-26 | Control method of duplex pump for transmission |
| PCT/CN2022/077544 WO2022179537A1 (en) | 2021-02-26 | 2022-02-24 | Method for controlling double-pump for transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110221050.2A CN112984090B (en) | 2021-02-26 | 2021-02-26 | Control method of duplex pump for transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112984090A true CN112984090A (en) | 2021-06-18 |
| CN112984090B CN112984090B (en) | 2023-01-06 |
Family
ID=76351356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110221050.2A Active CN112984090B (en) | 2021-02-26 | 2021-02-26 | Control method of duplex pump for transmission |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN112984090B (en) |
| WO (1) | WO2022179537A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022179537A1 (en) * | 2021-02-26 | 2022-09-01 | 中国第一汽车股份有限公司 | Method for controlling double-pump for transmission |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020105225A1 (en) * | 2001-02-07 | 2002-08-08 | Toyota Jidosha Kabushiki Kaisha | Hydraulic control apparatus of vehicle and control method |
| CN102493976A (en) * | 2011-12-01 | 2012-06-13 | 三一重工股份有限公司 | Power control system and control method for engineering machinery |
| CN207093614U (en) * | 2017-08-24 | 2018-03-13 | 中国第一汽车股份有限公司 | A kind of efficient oil supply system of automatic transmission |
| CN109237013A (en) * | 2018-10-08 | 2019-01-18 | 重庆长安汽车股份有限公司 | A kind of DCT transmission hydraulic control system, method and automobile |
| DE102017221637A1 (en) * | 2017-12-01 | 2019-06-06 | Zf Friedrichshafen Ag | Method and control device for operating a pump of a transmission |
| CN111828621A (en) * | 2020-07-22 | 2020-10-27 | 中国第一汽车股份有限公司 | Pressure control method of high-pressure system of automatic transmission |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3478271B2 (en) * | 2001-02-07 | 2003-12-15 | トヨタ自動車株式会社 | Hydraulic control device for automatic transmission for vehicles |
| JP2017067227A (en) * | 2015-10-01 | 2017-04-06 | ジヤトコ株式会社 | Control device and method of hydraulic circuit |
| CN206943363U (en) * | 2017-03-29 | 2018-01-30 | 湖南江麓容大车辆传动股份有限公司 | A kind of buncher hydraulic system |
| CN109084016B (en) * | 2018-10-08 | 2020-12-29 | 重庆长安汽车股份有限公司 | DCT transmission double-pump system, control method and automobile |
| CN112984090B (en) * | 2021-02-26 | 2023-01-06 | 中国第一汽车股份有限公司 | Control method of duplex pump for transmission |
-
2021
- 2021-02-26 CN CN202110221050.2A patent/CN112984090B/en active Active
-
2022
- 2022-02-24 WO PCT/CN2022/077544 patent/WO2022179537A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020105225A1 (en) * | 2001-02-07 | 2002-08-08 | Toyota Jidosha Kabushiki Kaisha | Hydraulic control apparatus of vehicle and control method |
| CN102493976A (en) * | 2011-12-01 | 2012-06-13 | 三一重工股份有限公司 | Power control system and control method for engineering machinery |
| CN207093614U (en) * | 2017-08-24 | 2018-03-13 | 中国第一汽车股份有限公司 | A kind of efficient oil supply system of automatic transmission |
| DE102017221637A1 (en) * | 2017-12-01 | 2019-06-06 | Zf Friedrichshafen Ag | Method and control device for operating a pump of a transmission |
| CN109237013A (en) * | 2018-10-08 | 2019-01-18 | 重庆长安汽车股份有限公司 | A kind of DCT transmission hydraulic control system, method and automobile |
| CN111828621A (en) * | 2020-07-22 | 2020-10-27 | 中国第一汽车股份有限公司 | Pressure control method of high-pressure system of automatic transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022179537A1 (en) * | 2021-02-26 | 2022-09-01 | 中国第一汽车股份有限公司 | Method for controlling double-pump for transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112984090B (en) | 2023-01-06 |
| WO2022179537A1 (en) | 2022-09-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109237013B (en) | DCT (discrete cosine transformation) transmission hydraulic control system and method and automobile | |
| KR101283950B1 (en) | Transmission hydraulic control system having a pump bypass valve | |
| CN109084016B (en) | DCT transmission double-pump system, control method and automobile | |
| JP5445045B2 (en) | Hydraulic control device for automatic transmission | |
| US8413437B2 (en) | Transmission hydraulic control system having independently controlled stator cooling flow | |
| SE515747C2 (en) | Hydraulic control system for a vehicle transmission | |
| US20140157766A1 (en) | Hydraulic Controller for an Automatic Transmission of a Motor Vehicle | |
| CN109826948B (en) | Hydraulic control system | |
| KR20150067172A (en) | External lube system for a transmission | |
| CN201973226U (en) | Hydraulic control system used for wet type automatic double-clutch transmission | |
| US11913542B2 (en) | Vehicle hydraulic control system and method | |
| CN112984090B (en) | Control method of duplex pump for transmission | |
| JP2007170462A (en) | Vehicular control device | |
| CN216643067U (en) | Hydraulic control device for wet-type double-clutch hybrid variable speed system | |
| JP6896168B2 (en) | Fluid system with accumulator for disc set pressing in steplessly adjustable winding transmission and steplessly adjustable winding transmission | |
| CN108779851B (en) | Hydraulic control device | |
| CN112360897A (en) | Common control clutch hydraulic control system and automobile | |
| CN218670565U (en) | Oil control system of hybrid transmission case and vehicle | |
| CN216478189U (en) | Hydraulic system and vehicle | |
| CN217002439U (en) | Hydraulic system of hybrid power gearbox | |
| CN212131113U (en) | Clutch oil circuit control system, transmission and loader | |
| CN113932006A (en) | Hydraulic control system of DHT (continuously variable Transmission) | |
| CN112943916A (en) | Hydraulic control system for automatic transmission and working equipment | |
| CN217874115U (en) | Anti-leakage low-loss hydraulic control mechanism of gearbox | |
| CN111271436A (en) | Transmission, transmission system and loader |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |