CN108757607B - Hydraulic system of hybrid transmission - Google Patents
Hydraulic system of hybrid transmission Download PDFInfo
- Publication number
- CN108757607B CN108757607B CN201810899548.2A CN201810899548A CN108757607B CN 108757607 B CN108757607 B CN 108757607B CN 201810899548 A CN201810899548 A CN 201810899548A CN 108757607 B CN108757607 B CN 108757607B
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- China
- Prior art keywords
- clutch
- pressure
- valve
- oil
- mechanical
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 23
- 239000003921 oil Substances 0.000 claims abstract description 87
- 238000001816 cooling Methods 0.000 claims abstract description 32
- 230000001105 regulatory effect Effects 0.000 claims abstract description 31
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 24
- 238000005461 lubrication Methods 0.000 claims abstract description 10
- 230000001050 lubricating effect Effects 0.000 claims description 16
- 230000000694 effects Effects 0.000 claims 1
- 230000001276 controlling effect Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
-
- 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
- F16H61/4043—Control of a bypass valve
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention discloses a hydraulic system of a hybrid transmission, which comprises: the hydraulic oil pump comprises an electronic pump, a mechanical pump, a cooling lubrication circuit and a main pressure oil circuit, wherein oil inlet ports of the electronic pump and the mechanical pump are connected with a hydraulic oil tank, the oil outlet port of the electronic pump is communicated with the cooling lubrication circuit, hydraulic oil is used for realizing cooling control on a motor and internal elements of a clutch through the cooling lubrication circuit, the oil outlet port of the mechanical pump is communicated with the main pressure oil circuit, high-pressure oil is supplied to the clutch through the main pressure oil circuit, a clutch pressure control circuit is communicated with the main pressure oil circuit, a pilot electromagnetic valve, a pressure regulating valve and a mechanical reversing valve are arranged on the clutch pressure control circuit, and the pressure regulating valve outputs stable pressure under the control of the pilot electromagnetic valve to complete clutch combination and is reversed through the mechanical reversing valve. Through the mode, the hydraulic system of the hybrid transmission adopts the low-cost VBS electromagnetic valve and the two mechanical reversing valves to realize accurate pressure adjustment in a low-pressure range, and can realize accurate pressure control in the low-pressure range.
Description
Technical Field
The invention relates to the technical field of hybrid transmissions, in particular to a hydraulic system of a hybrid transmission.
Background
The KISS POINT pressure value controlled by the clutch of the partially hybrid transmission is very low and is only 1-2 ar, the maximum combined pressure of the clutch reaches 1.5 mpa-2 mpa, and the accurate control of the KISS POINT POINT is difficult to realize by a direct-drive electromagnetic valve or a pilot electromagnetic valve and a single pressure regulating valve, so that gear shifting impact is easy to generate.
The eastern side of solar electric power generation is a hydraulic system developed by a certain hybrid transmission company in China, the control of a clutch of the hydraulic system adopts a direct-drive type proportional electromagnetic valve, the output control pressure range of the electromagnetic valve is 0-2 mpa, the sliding friction POINT of the clutch which needs to be accurately controlled in actual combination is about 1.5bar, and the actual test shows that the KISS POINT POINT is very close to the dead zone of the electromagnetic valve due to low pressure, so that the control is inaccurate and the impact is easy to generate.
At present, the proposal of adopting a direct drive type proportional electromagnetic valve on an automatic transmission is more and more, but for clutch control (KISS POINT is less than 10 percent of the control range of the electromagnetic valve) with special requirements, the direct drive electromagnetic valve obviously cannot meet the control requirements.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a hydraulic system of a hybrid transmission, which adopts a low-cost VBS electromagnetic valve and two mechanical reversing valves to realize accurate pressure adjustment in a low pressure range, meets the maximum pressure requirement of a clutch, can realize accurate pressure control in the low pressure range, and needs to ensure that the maximum pressure after the clutch is combined reaches a higher value.
In order to solve the technical problems, the invention adopts a technical scheme that: provided is a hybrid transmission hydraulic system including: an electronic pump, a mechanical pump, a cooling and lubricating loop and a main pressure oil way,
the oil inlets of the electronic pump and the mechanical pump are connected with a hydraulic oil tank, the oil outlet of the electronic pump is communicated with a cooling and lubricating loop, the hydraulic oil realizes cooling control on the motor and the internal elements of the clutch through the cooling and lubricating loop,
the oil outlet of the mechanical pump is communicated with a main pressure oil way, high-pressure oil is provided for the clutch through the main pressure oil way, the main pressure oil way is communicated with a clutch pressure control loop,
the clutch pressure control loop is provided with a pilot electromagnetic valve, a pressure regulating valve and a mechanical reversing valve, the pressure regulating valve outputs stable pressure under the control of the pilot electromagnetic valve to enable the clutch to be combined, and then the mechanical reversing valve is used for reversing, so that the clutch pressure is switched.
In a preferred embodiment of the present invention, the mechanical pump is connected to two clutches, a first clutch and a second clutch, through a main pressure oil path, and the mechanical pump supplies high-pressure oil to the first clutch and the second clutch, respectively, through the main pressure oil path.
In a preferred embodiment of the invention, a mechanically constant relief valve is provided in the main pressure line, through which the main pressure line provides stable hydraulic oil to the clutch pressure control circuit.
In a preferred embodiment of the present invention, the main pressure oil path is connected in parallel with a first clutch pressure control circuit and a second clutch pressure control circuit for delivering high pressure oil to the first clutch and the second clutch.
In a preferred embodiment of the invention, a first pilot electromagnetic valve and a first pressure regulating valve are arranged on an oil path of the first clutch pressure control loop to the first clutch, a first mechanical reversing valve is also arranged between the output end of the first pressure regulating valve and the first clutch,
the oil way of the second clutch pressure control loop leading to the second clutch is provided with a second pilot electromagnetic valve and a second pressure regulating valve, and a second mechanical reversing valve is arranged between the output end of the second pressure regulating valve and the second clutch.
In a preferred embodiment of the invention, the first pressure regulating valve and the second pressure regulating valve are respectively internally provided with a valve core and a spring, and the valve core and the spring can be adjusted to realize parameter adjustment.
In a preferred embodiment of the invention, a spool valve is arranged on the main pressure oil path, the spool valve is arranged at oil inlets of the first clutch pressure control loop and the second clutch pressure control loop, the spool valve is connected with a pilot proportional electromagnetic valve, and the spool valve is controlled by the pilot proportional electromagnetic valve to realize continuous adjustment of system pressure at 3-20 bar.
In a preferred embodiment of the present invention, a radiator is disposed on the cooling and lubricating circuit, and hydraulic oil in the cooling and lubricating circuit flows back to the hydraulic oil tank after passing through the radiator.
In a preferred embodiment of the invention, the first one-way valve is arranged at the oil outlet of the electronic pump, and the second one-way valve is arranged at the oil outlet of the mechanical pump.
In a preferred embodiment of the invention, the main pressure oil circuit is also provided with an overflow valve, an oil inlet of the overflow valve is communicated with the main pressure oil circuit, an oil outlet of the overflow valve is communicated with an oil return port of the hydraulic oil tank, and the overflow flow realizes cooling lubrication through the main pressure oil circuit.
The beneficial effects of the invention are as follows: the hydraulic system of the hybrid transmission adopts the low-cost VBS electromagnetic valve and the two mechanical reversing valves to realize accurate pressure adjustment in a low-pressure range, simultaneously meets the maximum pressure requirement of a clutch, can realize accurate pressure control in the low-pressure range, and simultaneously needs to ensure that the maximum pressure after the clutch is combined reaches a higher value.
Drawings
For a clearer description of the technical solutions of the embodiments of the present invention, the drawings that are needed in the description of the embodiments will be briefly introduced below, it being obvious that the drawings in the description below are only some embodiments of the present invention, and that other drawings can be obtained according to these drawings without inventive effort for a person skilled in the art, wherein:
FIG. 1 is a schematic diagram of a hybrid transmission hydraulic system of the present invention;
FIG. 2 is a pressure regulation and control graph of a clutch in a hybrid transmission hydraulic system of the present invention;
the components in the drawings are marked as follows: 100. the system comprises an electronic pump, 200, a mechanical pump, 300, a cooling and lubricating circuit, 301, a first one-way valve, 302, a radiator, 400, a main pressure oil circuit, 401, a second one-way valve, 402, a mechanical constant pressure reducing valve, 403, a slide valve, 404, a pilot proportional solenoid valve, 405, an overflow valve, 500, a first clutch pressure control circuit, 501, a first pilot solenoid valve, 502, a first pressure regulating valve, 503, a first mechanical reversing valve, 600, a second clutch pressure control circuit, 601, a second pilot solenoid valve, 602, a second pressure regulating valve, 603, a second mechanical reversing valve, 700, a first clutch, 800 and a second clutch.
Detailed Description
The following description of the technical solutions in the embodiments of the present invention will be clear and complete, and it is obvious that the described embodiments are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 1 to 2, an embodiment of the present invention includes:
a hybrid transmission hydraulic system comprising: the electronic pump 100, the mechanical pump 200, the cooling and lubricating circuit 300 and the main pressure oil circuit 400 are connected with hydraulic oil tanks through oil inlets of the electronic pump 100 and the mechanical pump 200.
The hybrid transmission hydraulic system employs dual oil pumps, one of the electronic pumps 100 and one of the mechanical pumps 200, the electronic pump 100 providing accurate cooling flow control for the motor and clutch internal components, the mechanical pump 200 providing the high pressure oil required for clutch control.
The first check valve 301 is provided at the oil outlet of the electronic pump 100 to prevent the backflow of hydraulic oil to the hydraulic tank when the mechanical pump 200 is operated alone.
The oil outlet of the electronic pump 100 is communicated with the cooling and lubricating loop 300, and hydraulic oil realizes cooling control on the motor and the internal elements of the clutch through the cooling and lubricating loop 300.
The cooling and lubricating circuit 300 is provided with a radiator 302, and hydraulic oil in the cooling and lubricating circuit 300 flows back to the hydraulic oil tank after passing through the radiator 302.
The oil outlet of the mechanical pump 200 is communicated with a main pressure oil way 400, high-pressure oil is provided for the clutch through the main pressure oil way 400, an overflow valve 405 is further arranged on the main pressure oil way 400, the oil inlet of the overflow valve 405 is communicated with the main pressure oil way 400, the oil outlet of the overflow valve 405 is communicated with the oil return port of the hydraulic oil tank, and the overflow flow realizes cooling lubrication through the main pressure oil way 400.
The cooling flow of the motor and the internal components of the clutch may be provided by controlling the rotational speed of the motor before the mechanical pump 200 is started;
after the mechanical pump 200 is started, the overflow flow provides cooling lubrication, and after the overflow flow meets the cooling lubrication flow, the electronic oil pump can be turned off to save energy, and the pressure of the cooling lubrication circuit 300 is realized through the load adjustment of each cooling lubrication point.
The second check valve 401 is arranged at the oil outlet of the mechanical pump 200, so that the hydraulic oil is prevented from flowing backwards to the hydraulic oil tank when the electronic pump works independently.
The main pressure oil path 400 is communicated with a clutch pressure control loop, a pilot electromagnetic valve, a pressure regulating valve and a mechanical reversing valve are arranged on the clutch pressure control loop, the pressure regulating valve outputs stable pressure under the control of the pilot electromagnetic valve to enable the clutch to be combined, and then the clutch pressure is switched through the mechanical reversing valve.
The mechanical pump 200 is connected to two clutches, namely, the first clutch 700 and the second clutch 800, through the main pressure oil path 400, and the mechanical pump 200 supplies high-pressure oil to the first clutch 700 and the second clutch 800, respectively, through the main pressure oil path.
Further, a mechanically constant pressure reducing valve 402 is provided on the main pressure oil path 400, and the main pressure oil path 400 supplies hydraulic oil of a stable pressure, about 6bar, to the clutch pressure control circuit through the mechanically constant pressure reducing valve 402.
The main pressure oil passage 400 is connected in parallel with a first clutch pressure control circuit 500 and a second clutch pressure control circuit 600 that supply high-pressure oil to the first clutch 700 and the second clutch 800.
The main pressure oil path 400 is provided with a slide valve 403, the slide valve 403 is arranged at oil inlets of the first clutch pressure control loop 500 and the second clutch pressure control loop 600, the slide valve 403 is connected with a pilot proportional electromagnetic valve 404, and the slide valve 403 is controlled by the pilot proportional electromagnetic valve 404 to realize continuous adjustment of the system pressure within 3-20 bar.
The first clutch pressure control circuit 500 is provided with a first pilot electromagnetic valve 501 and a first pressure regulating valve 502 on an oil path leading to the first clutch 700, and a first mechanical reversing valve 503 is also provided between an output end of the first pressure regulating valve 502 and the first clutch 700.
The oil path of the second clutch pressure control circuit 600 leading to the second clutch 800 is provided with a second pilot electromagnetic valve 601 and a second pressure regulating valve 602, and a second mechanical reversing valve 603 is also arranged between the output end of the second pressure regulating valve 602 and the second clutch 800.
Taking the first clutch 700 as an example, the first pressure regulating valve 502 can output a pressure of 0-4 bar under the control of the first pilot electromagnetic valve 501 (if other ranges are needed, the pressure can be realized by modifying the parameters of the valve core and the spring of the first pressure regulating valve 502), then the pressure is used for precisely controlling the KISS POINT of the first clutch 700, when the first clutch 700 is completely combined, the valve core of the first mechanical reversing valve 503 is reversed (the output control pressure of the electromagnetic valve is close to 10% of the upper limit at this time), and the pressure of the first clutch 700 is switched to the system pressure.
In the pressure control loop of the clutch, a mechanical reversing valve is added to realize the switching of the final pressure of the clutch, and when the vehicle stably runs, the system pressure can be properly reduced so as to achieve the aim of saving energy.
The KISS POINT POINT of clutch control can be easily realized by adjusting parameters of the pressure regulating valve according to actual requirements.
As shown in fig. 2, which is a pressure regulation and control diagram of the clutch, there are two curves, namely a full range clutch pressure regulation curve and a clutch pressure control curve:
taking the eastern scheme of solar electric power generation as an example, the output control pressure range of the direct-drive electromagnetic valve is 0-2 mpa, and the KISS POINT is near a dead zone (within 10% range) controlled by the electromagnetic valve at 1.5bar,KISS POINT POINT, so that the problem of incapability of controlling the accuracy is necessarily caused; the hydraulic system can set the KISS POINT POINT in the middle section of electromagnetic valve control, and the control is very accurate.
In terms of cost, the direct drive type proportional solenoid valve is almost twice the price of the pilot solenoid valve used in the invention, and the total cost is lower than that of the direct drive solenoid valve scheme although the invention adds two mechanical valve cores.
The hydraulic system of the hybrid transmission has the beneficial effects that:
the accurate control of the pressure can be realized in a low pressure range, meanwhile, the maximum pressure after the clutch is combined needs to be ensured to reach a higher value, and the KISS POINT POINT of the clutch control can be easily realized by adjusting the parameters of the pressure regulating valve according to actual requirements;
the accurate adjustment of the pressure in the low pressure range is realized by adopting a low-cost electromagnetic valve and two mechanical reversing valves, and meanwhile, the maximum pressure requirement of the clutch is met;
the final pressure of the clutch is switched, and when the vehicle runs stably, the system pressure can be properly reduced, so that the aim of saving energy is fulfilled.
The foregoing description is only illustrative of the present invention and is not intended to limit the scope of the invention, and all equivalent structures or equivalent processes or direct or indirect application in other related arts are included in the scope of the present invention.
Claims (6)
1. A hybrid transmission hydraulic system, comprising: an electronic pump, a mechanical pump, a cooling and lubricating loop and a main pressure oil way,
the oil inlets of the electronic pump and the mechanical pump are both connected with a hydraulic oil tank, the oil outlet of the electronic pump is communicated with a cooling and lubricating loop, the hydraulic oil realizes cooling control on the motor and the internal elements of the clutch through the cooling and lubricating loop, a radiator is arranged on the cooling and lubricating loop, the hydraulic oil in the cooling and lubricating loop flows back to the hydraulic oil tank after passing through the radiator,
the oil outlet of the mechanical pump is communicated with a main pressure oil way, high-pressure oil is provided for the clutch through the main pressure oil way, the main pressure oil way is communicated with a clutch pressure control loop,
the clutch pressure control loop is provided with a pilot electromagnetic valve, a pressure regulating valve and a mechanical reversing valve, the pressure regulating valve outputs stable pressure under the control of the pilot electromagnetic valve to complete the combination of the clutch, then the mechanical reversing valve is used for reversing, the switching of the clutch pressure is realized,
the mechanical pump is connected with two clutches, namely a first clutch and a second clutch, through a main pressure oil way, the mechanical pump provides high-pressure oil for the first clutch and the second clutch through the main pressure oil way,
the main pressure oil path is connected with a first clutch pressure control loop and a second clutch pressure control loop which are used for conveying high-pressure oil to the first clutch and the second clutch in parallel,
a first pilot electromagnetic valve and a first pressure regulating valve are arranged on an oil path of the first clutch pressure control loop leading to the first clutch, a first mechanical reversing valve is also arranged between the output end of the first pressure regulating valve and the first clutch,
the oil way of the second clutch pressure control loop leading to the second clutch is provided with a second pilot electromagnetic valve and a second pressure regulating valve, and a second mechanical reversing valve is arranged between the output end of the second pressure regulating valve and the second clutch.
2. The hybrid transmission hydraulic system of claim 1, wherein a mechanically-set relief valve is provided in the main pressure gallery, the main pressure gallery providing stable hydraulic oil to the clutch pressure control circuit through the mechanically-set relief valve.
3. The hybrid transmission hydraulic system of claim 1, wherein the first pressure regulating valve and the second pressure regulating valve are each provided with a valve element and a spring therein, the valve element and the spring being adjustable to effect parameter adjustment.
4. The hydraulic system of the hybrid transmission according to claim 1, wherein a spool valve is arranged on the main pressure oil path, the spool valve is arranged at oil inlets of the first clutch pressure control loop and the second clutch pressure control loop, the spool valve is connected with a pilot proportional solenoid valve, and the spool valve is controlled by the pilot proportional solenoid valve to realize continuous adjustment of system pressure within 3-20 bar.
5. The hybrid transmission hydraulic system of claim 1, wherein a first one-way valve is disposed at an outlet of the electronic pump and a second one-way valve is disposed at an outlet of the mechanical pump.
6. The hydraulic system of the hybrid transmission according to claim 1, wherein an overflow valve is further arranged on the main pressure oil path, an oil inlet of the overflow valve is communicated with the main pressure oil path, an oil outlet of the overflow valve is communicated with an oil return port of the hydraulic oil tank, and the overflow flow realizes cooling lubrication through the main pressure oil path.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810899548.2A CN108757607B (en) | 2018-08-09 | 2018-08-09 | Hydraulic system of hybrid transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810899548.2A CN108757607B (en) | 2018-08-09 | 2018-08-09 | Hydraulic system of hybrid transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108757607A CN108757607A (en) | 2018-11-06 |
| CN108757607B true CN108757607B (en) | 2023-11-07 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810899548.2A Active CN108757607B (en) | 2018-08-09 | 2018-08-09 | Hydraulic system of hybrid transmission |
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| CN (1) | CN108757607B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109538554B (en) * | 2018-11-20 | 2024-06-25 | 湖南科技大学 | Automobile, hydraulic system and control method thereof |
| CN111207161B (en) * | 2018-11-21 | 2021-09-07 | 宝沃汽车（中国）有限公司 | Hybrid electric vehicle, oil supply system, control method and control device of oil supply system |
| CN110778704B (en) * | 2019-10-25 | 2021-07-23 | 浙江吉利汽车研究院有限公司 | Hybrid power hydraulic system and vehicle |
| CN110864019B (en) * | 2019-11-28 | 2024-08-23 | 徐州海伦哲特种车辆有限公司 | Digital hydraulic leveling system of working platform of overhead working truck |
| CN111677851A (en) * | 2020-07-06 | 2020-09-18 | 泸州容大智能变速器有限公司 | Hydraulic system of hybrid power gearbox |
| CN111853228B (en) * | 2020-07-27 | 2021-11-12 | 浙江轩孚自动变速器有限公司 | Hydraulic control system of automatic transmission |
| CN113932006B (en) * | 2021-10-29 | 2022-12-27 | 蜂巢传动系统(江苏)有限公司保定研发分公司 | Hydraulic control system of DHT (continuously variable Transmission) |
| CN114001060A (en) * | 2021-11-15 | 2022-02-01 | 博格华纳汽车零部件(天津)有限公司 | Gearbox hydraulic system through feedback control |
| CN115182990B (en) * | 2022-06-06 | 2023-11-07 | 陕西法士特齿轮有限责任公司 | Hydraulic control system for hybrid hydraulic automatic gearbox |
| CN115076351A (en) * | 2022-07-06 | 2022-09-20 | 中国第一汽车股份有限公司 | Hydraulic control system |
| CN115450967B (en) * | 2022-09-09 | 2024-03-26 | 奇瑞汽车股份有限公司 | Hydraulic system for hybrid gearbox and automobile |
| CN115574089B (en) * | 2022-09-26 | 2024-06-14 | 重庆长安汽车股份有限公司 | Hybrid hydraulic control system, transmission and automobile |
| CN118030810A (en) * | 2022-11-01 | 2024-05-14 | 比亚迪股份有限公司 | Transmission hydraulic system, control method thereof and hybrid vehicle |
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| CN106593978A (en) * | 2015-10-14 | 2017-04-26 | 广州汽车集团股份有限公司 | Hybrid electric vehicle and motor cooling hydraulic system thereof |
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|---|---|---|---|---|
| CN103502695A (en) * | 2011-05-06 | 2014-01-08 | 奥迪股份公司 | Clutch transmission |
| CN103192821A (en) * | 2013-03-30 | 2013-07-10 | 长城汽车股份有限公司 | Hybrid power hydraulic control system |
| CN106593978A (en) * | 2015-10-14 | 2017-04-26 | 广州汽车集团股份有限公司 | Hybrid electric vehicle and motor cooling hydraulic system thereof |
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| CN208778370U (en) * | 2018-08-09 | 2019-04-23 | 江苏金润汽车传动科技有限公司 | Mixed dynamic transmission pressure system |
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| CN108757607A (en) | 2018-11-06 |
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