CN110319181B - Hydraulic gear shifting and cooling lubrication system for hybrid power gearbox - Google Patents
Hydraulic gear shifting and cooling lubrication system for hybrid power gearbox Download PDFInfo
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- CN110319181B CN110319181B CN201910534937.XA CN201910534937A CN110319181B CN 110319181 B CN110319181 B CN 110319181B CN 201910534937 A CN201910534937 A CN 201910534937A CN 110319181 B CN110319181 B CN 110319181B
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- 238000001816 cooling Methods 0.000 title claims abstract description 73
- 238000005461 lubrication Methods 0.000 title claims abstract description 21
- 239000003921 oil Substances 0.000 claims abstract description 535
- 239000010687 lubricating oil Substances 0.000 claims abstract description 38
- 230000005540 biological transmission Effects 0.000 claims abstract description 26
- 239000007788 liquid Substances 0.000 claims abstract description 15
- 230000001050 lubricating effect Effects 0.000 claims abstract description 12
- 230000017525 heat dissipation Effects 0.000 claims abstract description 7
- 230000001105 regulatory effect Effects 0.000 claims description 26
- 230000001276 controlling effect Effects 0.000 claims description 17
- 238000000926 separation method Methods 0.000 abstract 1
- 230000009286 beneficial effect Effects 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 238000001914 filtration Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
Classifications
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
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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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
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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
- 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
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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
- 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
- F16H57/0441—Arrangements of pumps
Abstract
The invention relates to the technical field of hybrid power transmissions, and discloses a hydraulic gear shifting system and a cooling lubrication system for a hybrid power transmission, wherein an oil supply system comprises an integrated double-oil-outlet filter screen, a mechanical pump, an electronic pump and a first small-flow switch electromagnetic valve, wherein the mechanical pump is communicated with a main oil way, and oil liquid of the electronic pump can be communicated with the main oil way or a cold lubrication oil way through the control of an oil pump switching valve to realize controllable high-low pressure separation; the hydraulic gear shifting system comprises a main oil way, a main oil way oil pressure control module and a gear shifting module, wherein the gear shifting module is provided with a redundant reversing valve, so that the gear shifting safety and reliability are improved; the cooling and lubricating system comprises a heat dissipation module, an oil size circulation control module and an oil distribution module, so that good control of oil temperature is realized, and cooling and lubricating oil is distributed more accurately. Compared with the prior art, the invention is more suitable for the diesel E-CVT hybrid transmission, avoids the oil robbing phenomenon of the double oil pumps, and is safer and more reliable when electrical faults occur.
Description
Technical Field
The invention relates to the technical field of automatic transmissions, in particular to a hydraulic gear shifting and cooling lubrication system for a diesel power split-type hybrid transmission (E-CVT).
Background
With the increasing national laws of automobile fuel consumption and emission, light commercial vehicles face severe situations. At present, aiming at the working characteristics of a diesel engine, a hybrid power gearbox which is matched with the diesel engine is developed, and the oil consumption and the emission of a power system can be optimized to the greatest extent. The E-CVT hybrid transmission is a planetary gear set power split device, and is distinguished from a conventional CVT continuously variable transmission. The hybrid transmission adopts an E-CVT architecture, so that driving comfort can be improved.
The E-CVT hybrid gearbox needs a hydraulic gear shifting system to realize automatic gear shifting of the whole vehicle, and each gear is switched through two clutches and two multimode brakes which are connected with an engine and a motor in a planetary row. And under the hybrid power mode, the combination and disconnection of different clutches can be controlled to ensure that the engine and the motor jointly bear the torque requirement of the whole vehicle, the working range of the engine is regulated and optimized, the oil consumption and emission of the system are reduced, and the dynamic property of the system is improved.
The E-CVT hybrid transmission of the prior art has a number of disadvantages: for example, a motor, a clutch, a bearing, a planet row and the like of the E-CVT hybrid transmission need cooling and lubrication, and because the cooling load is increased, the cooling and lubrication flow needs to be accurately calculated, the design of an oil supply system in the prior art is unreasonable, the external pressure drop is large when the environment is at low temperature, excessive cooling oil passes through external circulation, and the temperature of the oil is slowly raised; for example, in the prior art, the oil pump of the cooling and lubricating oil circuit and the oil pump of the main oil circuit of the gearbox can have the phenomenon of oil robbing during working, so that the filtering load of an oil outlet filter screen is increased; also for example, the E-CVT hybrid transmission mechanically does not allow simultaneous closing of the clutches and multimode brakes, but when the vehicle fails electrically, the clutches and multimode brakes of the prior art hydraulic shifting system can simultaneously close, resulting in case damage.
Disclosure of Invention
Accordingly, the present invention is directed to a hydraulic shifting and cooling lubrication system for a hybrid transmission, which solves the problems of the prior art.
In order to achieve the above purpose, the invention adopts the following technical scheme:
a hydraulic pressure gear shift and cooling lubrication system for hybrid transmission, characterized by that includes oil feeding system, hydraulic pressure gear shift system and cooling lubrication system, wherein:
the oil supply system comprises a double-oil-outlet filter screen, a mechanical pump, an electronic pump, an oil pump switching valve and a first small-flow switching electromagnetic valve for controlling the oil pump switching valve, wherein a first oil outlet of the double-oil-outlet filter screen is communicated with a main oil way through the mechanical pump, a second oil outlet of the double-oil-outlet filter screen is communicated with the electronic pump, and the electronic pump is communicated with the main oil way or a cooling and lubricating oil way through the oil pump switching valve; the oil pump switching valve is provided with a first working position and a second working position, the oil pump switching valve is controlled to work in the first working position or the second working position through the first small-flow switching electromagnetic valve, when the oil pump switching valve is positioned in the first working position, the oil pump switching valve guides the flow of the electronic pump to the cooling lubricating oil way, and when the oil pump switching valve is positioned in the second working position, the oil pump switching valve guides the flow of the electronic pump to the main oil way; the hydraulic gear shifting system comprises the main oil way and a gear shifting module; the cooling and lubricating system comprises a heat dissipation module.
As a preferable technical scheme, an oil outlet of the mechanical pump is communicated with a main oil way, and the flow of the main oil way is led to the hydraulic gear shifting system; an oil outlet of the electronic pump is communicated with an oil inlet of the oil pump switching valve, a first oil outlet of the oil pump switching valve is communicated with a cooling and lubricating oil circuit, and the flow of the cooling and lubricating oil circuit is led to the cooling and lubricating system; the second oil outlet of the oil pump switching valve is communicated with the main oil way, the control port of the oil pump switching valve is communicated with the oil outlet of the first small flow switching electromagnetic valve, the oil inlet of the first small flow switching electromagnetic valve is connected with the main oil way, and the oil drain port of the first small flow switching electromagnetic valve is connected with an oil return pipeline.
Further preferably, the oil supply system further comprises a first one-way valve, a mechanical pump relief valve, a second one-way valve 8; an oil outlet of the mechanical pump 3 is communicated with a main oil way through the second one-way valve, and an oil outlet of the electronic pump is communicated with an oil inlet of the oil pump switching valve through the first one-way valve; and an oil inlet of the mechanical pump safety valve is communicated with a pipeline between the second one-way valve and an oil outlet of the mechanical pump, and the oil outlet of the mechanical pump safety valve is connected with an oil return pipeline.
The double-oil-outlet integrated filter screen of the oil supply system is provided with the double oil outlets, so that the phenomenon of oil robbing of two oil pumps is avoided when the rotation speed of one oil pump rises rapidly.
Under the hybrid power working condition, the mechanical pump provides oil for the main oil way, and the coil current of the first small-flow switching electromagnetic valve is controlled, so that the oil pump switching valve is controlled to be in a first working position or a second working position, and the oil flow direction of the electronic pump is changed according to the system requirement, so that the flow requirement of the main oil way is ensured, and the energy consumption is reduced. Under very few working conditions, the mechanical pump can independently bear the oil requirement of the main oil way and the cooling lubricating oil requirement, and the electronic pump stops working. The first check valve avoids the situation that oil flows back into the electronic pump. Under the pure electric working condition, the electronic pump works, the mechanical pump does not work, the electromagnetic coil current of the first small-flow electromagnetic valve is controlled, the oil pump switching valve is in the first working position, and the electronic pump independently bears the pressure flow requirements of the main oil way and the cooling and lubricating oil way.
As a preferable technical scheme, the hydraulic gear shifting system further comprises a main oil way oil pressure control module, wherein the main oil way oil pressure control module comprises a pressure limiting valve communicated with the main oil way, a first small flow proportional electromagnetic valve communicated with the pressure limiting valve, and a main pressure regulating mechanical valve communicated with the first small flow proportional electromagnetic valve; the pressure limiting valve reduces the oil pressure of the main oil way to a certain value and then inputs the oil pressure to the first small-flow proportional electromagnetic valve, so that the electromagnetic valve can be prevented from being damaged by the excessive oil pressure; controlling the valve core opening of the main pressure regulating mechanical valve through a first small flow proportional electromagnetic valve to control the oil pressure of the main oil way; the accumulator is arranged in a pilot oil path of the main oil path oil pressure control module.
Further preferably, an oil outlet of the pressure limiting valve is communicated with an oil inlet of the first small-flow proportional electromagnetic valve; the first control port of the main pressure regulating mechanical valve is communicated with the main oil way, the second control port of the main pressure regulating mechanical valve is communicated with the output port of the first small flow proportional electromagnetic valve, and the valve core of the main pressure regulating mechanical valve enables the oil inlet of the main pressure regulating mechanical valve to be communicated with the oil outlet with different valve core openings under the action of the oil pressure of the first control port and the second control port, so that the oil pressure of the main oil way is ensured to be at a control value; and a piston cavity of the energy accumulator is communicated with a second control port of the main pressure regulating mechanical valve and an output port of the first small-flow proportional electromagnetic valve.
The oil inlet of the first small-flow proportional electromagnetic valve is communicated with different valve core openings of the output port by controlling the electromagnetic coil current of the first small-flow proportional electromagnetic valve, so that the oil pressure of the output port is ensured to be a control value; under the action of the first control port and the second control port, the valve core of the main pressure regulating mechanical valve enables the oil inlet and the oil outlet to be communicated with different valve core openings, and the oil pressure of the main oil way is ensured to be at a control value. The accumulator is arranged in the pilot oil way of the main oil way oil pressure control module, so that the oil pressure fluctuation of the system can be relieved, the pressure and cavity requirements of the accumulator are reduced, and the arrangement space of the whole hydraulic system is saved.
In some preferred embodiments, the shift module of the present invention includes a first clutch, a second clutch, a first multimode brake, a second multimode brake, a first high flow proportional solenoid valve controlling the first clutch, a second high flow proportional solenoid valve controlling the second clutch, a first clutch redundancy check valve, two second low flow switching solenoid valves controlling the first multimode brake, a first multimode brake redundancy check valve, and a third low flow switching solenoid valve controlling the second multimode brake; an oil inlet of the first clutch redundancy reversing valve is communicated with the main oil way, an oil outlet of the first clutch redundancy reversing valve is communicated with a piston cavity of the first clutch through the second large-flow proportional electromagnetic valve, and two control ports of the first clutch redundancy reversing valve are correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multimode brake respectively; two oil inlets of the first multi-mode brake redundant reversing valve are respectively communicated with the two second small-flow switching electromagnetic valves, and two oil outlets of the first multi-mode brake redundant reversing valve are respectively correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multi-mode brake; the control port of the first multimode-brake redundant reversing valve is in communication with the piston cavity of the first clutch.
Preferably, an oil inlet of the first large-flow proportional electromagnetic valve is communicated with the main oil way, an oil drain port is connected with an oil return pipeline, and an oil outlet is communicated with a piston cavity of the first clutch; an oil inlet of the second large-flow proportional electromagnetic valve is communicated with an oil outlet of the first clutch redundancy reversing valve, an oil discharge port is connected with an oil return pipeline, and the oil outlet is communicated with a piston cavity of the first clutch; an oil inlet of one of the second small flow switching electromagnetic valves is communicated with the main oil way, an oil drain port is connected with the oil return pipeline, and an oil outlet is communicated with a first oil inlet of the first multi-mode brake redundancy reversing valve; an oil inlet of the other second small flow switching electromagnetic valve is communicated with the main oil way, an oil drain port is connected with an oil return pipeline, and an oil outlet is communicated with a second oil inlet of the first multi-mode brake redundant reversing valve; an oil inlet of the third small-flow switching electromagnetic valve is communicated with the main oil way, an oil drain port is connected with the oil return pipeline, a first oil outlet is communicated with a forward locking piston cavity of the second multimode brake, and a second oil outlet is communicated with a reverse locking piston cavity of the second multimode brake.
In some preferred embodiments, the hydraulic shift and cooling lubrication system further comprises a park module comprising a small flow on-off solenoid valve and a park mechanism; the parking mechanism comprises an electromagnetic safety lock, an oil inlet of a small-flow switch electromagnetic valve of the parking mechanism is controlled to be communicated with the main oil way, an oil discharge port is connected with an oil return pipeline, and an oil outlet is communicated with a piston cavity of the parking mechanism.
In some preferred embodiments, the heat dissipation module comprises a radiator, and the cooling and lubrication system further comprises an oil size circulation control module and an oil distribution module; the oil liquid size circulation control module comprises an overflow valve and a bypass valve, and the overflow valve is communicated with the cooling and lubricating oil way and an oil inlet of the mechanical pump; the oil inlet of the radiator and the oil inlet of the bypass valve are connected in parallel with the bypass valve and the radiator in the cooling and lubricating oil path, and the oil outlet of the radiator is communicated with the oil outlet of the bypass valve and the oil distribution module. Specifically, a first port of the overflow valve is communicated with a first oil outlet of the oil pump switching valve, an oil outlet of the main pressure regulating mechanical valve, an oil inlet of the bypass valve and an oil inlet of the radiator, and a second port of the overflow valve is communicated with an oil inlet of the mechanical pump.
In some preferred embodiments, the oil distribution module comprises: three primary cooling lubricating oil liquid distribution restrictors, a plurality of secondary cooling lubricating oil liquid distribution restrictors and a plurality of tertiary cooling lubricating oil liquid distribution restrictors; and an oil outlet of the radiator is communicated with an oil outlet of the bypass valve and the three primary cooling lubricating oil distributing restrictors.
The bypass valve is accurately designed to open valve pressure, so that most of the cooling lubricating oil liquid passes through the bypass valve at low temperature to carry out small circulation, the oil liquid is beneficial to quickly heating up, and at high temperature, the cooling lubricating oil liquid passes through the radiator to carry out external large circulation, and the temperature of the oil liquid is controlled not to exceed the temperature. At low temperature, the pressure drop of the radiator and the bypass valve is high, so that the radiator is protected, the overflow valve is opened, and part of oil returns to the oil pumping port of the mechanical pump. The precise design of the primary, secondary and tertiary restrictors for cooling and lubricating oil ensures that the oil is sufficient at each cooling and lubricating part of the E-CVT hybrid transmission when the system flows.
By adopting the technical scheme, the invention achieves the following beneficial effects.
The oil supply system is applied to oil supply of the hydraulic system of the E-CVT hybrid transmission, meets the flow and pressure requirements of the whole transmission in each gear, reduces the energy consumption of the hydraulic system, solves the problem of oil robbing during double-oil pump operation, overflows oil into an oil suction port of the oil pump, and reduces the filtering load of a filter screen.
The hydraulic gear shifting system is applied to gear control of an E-CVT hybrid power gearbox, can realize smooth running of 9 gears, can adjust the working range of an engine in a large range, and can reduce oil consumption and emission of the whole vehicle. Meanwhile, the mechanical structure of the E-CVT hybrid transmission does not allow the clutch and the multimode brake to be closed at the same time, and the redundant reversing valve performs double protection on a hydraulic system, so that the simultaneous combination of the clutch and the multimode brake caused by electrical faults is avoided, and the case body is damaged.
The cooling and lubricating system is applied to cooling and lubricating control of the E-CVT hybrid transmission, and flow supply is more accurate through accurate design of a plurality of primary, secondary and tertiary restrictors of cooling and lubricating oil. The bypass valve and the radiator enable the oil in the gearbox to be heated up rapidly at low temperature, and the oil temperature is better controlled not to exceed the limit at high temperature. The overflow valve protects the radiator from overpressure damage.
The hydraulic gear shifting and cooling lubricating system for the hybrid power gearbox provided by the invention aims at a plurality of problems and defects existing in the prior art, is reasonable in design, is provided with the oil dividing orifice, is additionally provided with the bypass valve before the oil dividing way, is connected with the radiator outside the gearbox in parallel, can reduce the external pressure drop at low temperature, and simultaneously solves the problems that when the ambient temperature is low, excessive cooling oil passes through the external circulation and the temperature of the oil is slow to rise, and is particularly suitable for the diesel E-CVT hybrid power gearbox, and has wide application prospect and huge commercial value.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system of the present invention;
fig. 2 is a shift logic diagram of the present invention.
Detailed Description
The following detailed description of the invention is presented in conjunction with the drawings to provide those skilled in the art with a better understanding of the advantages and features of the invention, and to provide a clearer and more accurate definition of the scope of the invention.
As shown in fig. 1, a hydraulic gear shifting and cooling lubrication system for a hybrid transmission of the present embodiment is characterized by comprising an oil supply system, a hydraulic gear shifting system and a cooling lubrication system. The hydraulic gear shifting system comprises a main oil way, a main oil way oil pressure control module and a gear shifting module; the cooling and lubricating system comprises a heat dissipation module, an oil size circulation control module and an oil distribution module, wherein the heat dissipation module comprises a radiator 11.
The oil supply system supplies flow and pressure to the whole E-CVT hybrid gearbox oil pressure system. The oil supply system comprises a double-oil-outlet filter screen 2, a mechanical pump 3 driven by an engine, an electronic pump 4 driven by a motor, a first one-way valve 5, an oil pump switching valve 6, a mechanical pump safety valve 7, a second one-way valve 8 and a first small-flow switching electromagnetic valve 13 for controlling the oil pump switching valve 6, wherein a first oil outlet of the double-oil-outlet filter screen 2 is communicated with a main oil circuit 100 through the mechanical pump 3 via the second one-way valve 8, a second oil outlet of the double-oil-outlet filter screen 2 is communicated with the electronic pump 4, and an oil outlet of the electronic pump 4 is communicated with an oil inlet B1 of the oil pump switching valve 6 via the first one-way valve 5. An oil inlet of the mechanical pump safety valve 7 is communicated with a pipeline between the second one-way valve 8 and an oil outlet of the mechanical pump 3, and the oil outlet of the mechanical pump safety valve 7 is connected with an oil return pipeline.
The oil outlet of the mechanical pump 3 is communicated with a main oil way 100, and the flow of the main oil way 100 is led to the hydraulic gear shifting system; an oil outlet of the electronic pump 4 is communicated with an oil inlet B1 of the oil pump switching valve 6. The oil pump switching valve 6 has a first operating position and a second operating position, and the oil pump switching valve 6 is controlled to operate in the first operating position or the second operating position by the first small flow switching solenoid valve 13. When the oil pump switching valve 6 is in the first working position, the oil inlet B1 of the oil pump switching valve 6 is communicated with the first oil outlet A1, and the oil pump switching valve 6 directs the flow of the electronic pump 4 to the cooling and lubrication oil path 200. When the oil pump switching valve 6 is in the second working position, the oil inlet B1 of the oil pump switching valve 6 is communicated with the second oil outlet A2, and the oil pump switching valve 6 guides the flow of the electronic pump 4 to the main oil path 100. The control end D1 of the oil pump switching valve 6 is communicated with the oil outlet A3 of the first small flow switching electromagnetic valve 13, the oil inlet B1 of the first small flow switching electromagnetic valve 13 is connected with the main oil way 100, and the oil outlet B3 of the first small flow switching electromagnetic valve 13 is connected with the oil return pipeline.
The main oil way oil pressure control module comprises a pressure limiting valve 14 communicated with a main oil way 100, a first small flow proportional electromagnetic valve 15 communicated with the pressure limiting valve 14, and a main pressure regulating mechanical valve 9 communicated with the first small flow proportional electromagnetic valve 15; the oil inlet of the pressure limiting valve 14 is communicated with the main oil way 100, the oil outlet A4 of the pressure limiting valve 14 is communicated with the oil inlet B11 of the first small flow proportional electromagnetic valve 15, and the oil outlet B12 of the first small flow proportional electromagnetic valve 15 is connected with the oil return pipeline. The first control port D2 of the main regulator valve 9 communicates with the main oil passage 100, and the second control port D3 communicates with the output port A9 of the first small flow rate proportional solenoid valve 15.
In this embodiment, the mechanical pump 3 and the electronic pump 4 work respectively or simultaneously according to different working condition requirements of the system, and only the electronic pump 4 works under the pure electric working condition, the oil supplied by the electronic pump 4 is communicated with the oil inlet B1 of the oil pump switching valve 6 through the one-way valve 5, the oil inlet B1 of the oil pump switching valve 6 is communicated with the second oil outlet A2, the second oil outlet A2 is connected with the main oil way 100, and the pressure establishment of the main oil way is completed; the oil inlet B16 of the main pressure regulating mechanical valve 9 is communicated with the main oil way 100, the oil inlet B16 and the oil outlet A13 are communicated with each other by a certain valve core opening degree under the oil pressure action of a first control port D2 and a second control port D3 of the main pressure regulating mechanical valve 9, and oil is led to the cooling and lubricating oil way 200. When the hybrid power working condition is adopted, the mechanical pump 3 works, the electronic pump 4 can work or not work according to the flow requirement of the hydraulic system, the output flow is changed through the rotation speed adjustment of the oil pump motor (EM motor) when the electronic pump 4 works, if the flow supplied to the main oil way 100 by the mechanical pump 3 meets the pressure building requirement, the electromagnetic coil current of the first small flow switching electromagnetic valve 13 is controlled, the oil inlet B2 of the first small flow switching electromagnetic valve 13 is communicated with the oil outlet A3, the control port D1 of the oil pump switching valve 6 is communicated with the oil outlet A3 of the first small flow switching electromagnetic valve 13, the oil pressure of the control port D1 enables the valve core of the oil pump switching valve 6 to act, the oil inlet B1 port is communicated with the first oil outlet A1, and the oil of the electronic pump 4 enters the cooling and lubricating oil way 200, so that the energy consumption of the system is reduced; when the mechanical pump 3 and the electronic pump 4 work simultaneously, working conditions of abrupt rising of the rotating speed are all generated, and the problem that the mechanical pump 3 and the electronic pump 4 mutually rob oil under the working conditions is solved by the double oil outlets of the integrated double oil outlet filter screen 2.
The pressure limiting valve 14 reduces the oil pressure of the main oil path 100 to a certain value and inputs the oil pressure to the first small flow rate proportional electromagnetic valve 15, so that the first small flow rate proportional electromagnetic valve 15 can be prevented from being damaged by the excessively high oil pressure; the valve element opening degree of the main pressure regulating mechanical valve 9 is controlled by the first small flow rate proportional solenoid valve 15 to control the oil pressure of the main oil passage 100. Specifically, under the oil pressure action of the first control port D2 and the second control port D3, the valve cores of the main pressure regulating mechanical valve 9 enable the oil inlet B16 and the oil outlet a13 of the main pressure regulating mechanical valve 9 to be communicated with different valve core openings, so that the oil pressure of a main oil way is ensured to be at a control value; the piston cavity of the accumulator 16 is communicated with the second control port D3 of the main pressure regulating mechanical valve 9 and the output port A9 of the first small flow proportional solenoid valve 15.
The oil inlet B11 of the first small-flow proportional electromagnetic valve 15 is communicated with different valve core openings of the output port A9 by controlling the electromagnetic coil current of the first small-flow proportional electromagnetic valve 15, so that the oil pressure of the output port A9 is ensured to be a control value; under the action of the first control port D2 and the second control port D3, the valve cores of the main pressure regulating mechanical valve 9 enable the oil inlet B16 and the oil outlet A13 to be communicated with different valve core openings, and the oil pressure of the main oil way 100 is ensured to be at a control value. The accumulator 16 is arranged in a pilot oil way of the main oil way oil pressure control module, so that the oil pressure fluctuation of the system can be relieved, the pressure and cavity requirements of the accumulator 16 are reduced, and the arrangement space of the whole hydraulic system is saved.
The hydraulic shift system controls gear control of the E-CVT hybrid gearbox. As shown in fig. 1 and 2, the shift module in the hydraulic shift system includes a C0 clutch, a C1 clutch 29, a BE1 multimode brake 22, and a BE2 multimode brake 23, where the CO clutch is a first clutch 27, the C1 clutch is a second clutch 29, the BE1 multimode brake is a first multimode brake 22, and the BE2 multimode brake is a second multimode brake 23 for convenience of distinction.
The shift module further includes a first high flow proportional solenoid valve 28 that controls a first clutch 29, a second high flow proportional solenoid valve 26 that controls a second clutch, a first clutch redundancy check valve 21, two second low flow switching solenoid valves 18, 19 that control a first multimode brake 22, a first multimode brake redundancy check valve 20, and a third low flow switching solenoid valve 17 that controls a second multimode brake 23. The specific connection of the components is described in detail below.
The oil inlet B23 of the first large-flow proportional solenoid valve 28 is communicated with the main oil way 100, the oil outlet B24 is connected with an oil return pipeline, and the oil outlet A18 is communicated with a piston cavity of the first clutch 29.
The oil inlet B21 of the second large-flow proportional electromagnetic valve 26 is communicated with the oil outlet A10 of the first clutch redundancy reversing valve 21, the oil outlet B22 is connected with an oil return pipeline, and the oil outlet A17 is communicated with a piston cavity of the first clutch 27.
The oil inlet B13 of the first clutch redundancy reversing valve 21 is communicated with the main oil way 100, the oil outlet A10 is communicated with the piston cavity of the first clutch 27 through the second high-flow proportional electromagnetic valve 26, and the two control ports D6 and D7 of the first clutch redundancy reversing valve 21 are respectively correspondingly communicated with the forward locking piston cavity and the reverse locking piston cavity of the first multimode brake 22.
The two oil inlets B14 and B15 of the first multi-mode brake redundancy reversing valve 20 are respectively communicated with the two second small flow switching electromagnetic valves 18 and 19, and the two oil outlets A11 and A12 are respectively correspondingly communicated with the forward locking piston cavity and the reverse locking piston cavity of the first multi-mode brake 22. The control port D5 of the first multimode-brake redundancy directional valve 20 communicates with the piston chamber of the first clutch 27.
An oil inlet B8 of one second small flow switching electromagnetic valve 18 is communicated with the main oil way 100, an oil drain port B7 is connected with an oil return pipeline, and an oil outlet A7 is communicated with a first oil inlet B14 of a first multi-mode brake redundancy reversing valve 20.
The oil inlet B10 of the other second small flow switching electromagnetic valve 19 is communicated with the main oil way 100, the oil drain port B9 is connected with an oil return pipeline, and the oil outlet A8 is communicated with the second oil inlet B15 of the first multi-mode brake redundancy reversing valve 20.
The oil inlet B5 of the third small flow switch electromagnetic valve 17 is communicated with the main oil way 100, the oil drain port B6 is connected with an oil return pipeline, the first oil outlet A5 is communicated with a forward locking piston cavity of the second multimode brake 23, and the second oil outlet A6 is communicated with a reverse locking piston cavity of the second multimode brake 23.
When the first multimode brake 22 does not have locking action, the port of the oil inlet B8 of the second small-flow switching electromagnetic valve 18 is communicated with the oil outlet A7, the oil inlet B9 of the second small-flow switching electromagnetic valve 19 is communicated with the oil outlet A8, at the moment, the first clutch redundancy reversing valve 21 works in the middle position, the oil inlet B13 is communicated with the oil outlet A10, namely, the communication of the main oil way 100 with the oil inlet B21 of the second large-flow proportional electromagnetic valve 26 is realized, the coil current of the second large-flow proportional electromagnetic valve 26 is controlled, the oil inlet B21 is communicated with the oil outlet A17, the oil outlet A17 reaches control pressure, and the first clutch 27 completes combining action. When the first multimode brake 22 is locked clockwise, the oil inlet B8 of the second small-flow switching electromagnetic valve 18 is communicated with the oil outlet A7, the oil inlet B9 of the second small-flow switching electromagnetic valve 19 is communicated with the oil outlet A8, at this time, the control port D7 of the first clutch redundancy reversing valve 21 is the same as the oil pressure of the forward locking piston cavity of the first multimode brake 22, the valve core moves, the first clutch redundancy reversing valve 21 works in the right position, the oil inlet B13 is blocked from the oil outlet a10, the main oil way 100 cannot be communicated with the oil inlet B21 of the second large-flow proportional electromagnetic valve 26, and even if the coil of the second large-flow proportional electromagnetic valve 26 receives current, the first clutch 27 cannot be closed.
When the first multimode brake 22 is locked, the HCU (Hybrid Control Unit, hybrid vehicle controller) failure or electromagnetic interference may cause the coil of the second high flow proportional solenoid valve 26 to receive current, and the first clutch 27 is closed, resulting in damage to the transmission. Therefore, the invention effectively avoids the occurrence of the fault and improves the safety and reliability of the E-CVT hybrid transmission.
When the first clutch 27 is not closed, the coil of the second large-flow proportional electromagnetic valve 26 is not electrified, the second large-flow proportional electromagnetic valve 26 works at the left position, the oil outlet A17 is communicated with the oil drain B22 and is connected with an oil return pipeline, the control port D5 of the first multi-mode brake redundancy reversing valve 20 is communicated with the oil outlet A17, the control port D5 is free from oil pressure, the first multi-mode brake redundancy reversing valve 20 works at the right position, the first oil inlet B14 is communicated with the first oil outlet A11, and the second oil inlet B15 is communicated with the second oil outlet A12; if the electromagnetic coil of the second small flow switching electromagnetic valve 19 receives current, the oil inlet B10 is communicated with the oil outlet A8, and the first multimode brake 22 is reversely locked; if the electromagnetic coil of the second small flow switching electromagnetic valve 18 receives current, the oil inlet B8 of the second small flow switching electromagnetic valve 18 is communicated with the oil outlet A7, and the first multimode brake 22 is locked positively.
When the first clutch is closed, a coil of the second high-flow proportional electromagnetic valve 26 receives current, the second high-flow proportional electromagnetic valve 26 works at the right position, the oil outlet A17 is communicated with the oil inlet B21, the control port D5 of the first multi-mode brake redundancy reversing valve 20 is communicated with the oil outlet A17, the oil pressure of the control port D5 pushes the valve core, the first multi-mode brake redundancy reversing valve 20 works at the left position, the first oil inlet B14 is cut off from the first oil outlet A11, and the second oil inlet B15 port is cut off from the second oil outlet A12; at this time, the first multimode actuator 22 is not locked in the forward direction or the reverse direction regardless of the current received by the solenoid of the second small flow switching solenoid valve 18 and the solenoid of the second small flow switching solenoid valve 19 due to the HCU failure or electromagnetic interference. Therefore, the present invention avoids the simultaneous closing failure of the first clutch 27 and the first multimode brake 22 due to the HCU failure or electromagnetic interference, and improves the reliability and safety of the E-CVT hybrid transmission.
The oil inlet B23 of the first large-flow proportional electromagnetic valve 28 controlling the second clutch 29 is communicated with the main oil way 100, the oil drain port B24 is connected with an oil return pipeline, the oil outlet A18 is communicated with a piston cavity of the second clutch 29, the coil of the first large-flow proportional electromagnetic valve 28 is controlled to receive current, the first large-flow proportional electromagnetic valve 28 works at the right position, the oil inlet B23 is communicated with the oil outlet A18, and the second clutch 29 is closed.
The oil inlet B5 of the third small flow switch electromagnetic valve 17 controlling the second multimode brake 23 is communicated with the main oil way 100, the oil drain port B6 is connected with an oil return pipeline, the first oil outlet A5 is communicated with an unlocking piston cavity of the second multimode brake 23, and the second oil outlet A6 is communicated with a reverse locking piston cavity of the second multimode brake 23. When the coil of the third small flow switching electromagnetic valve 17 is controlled to be free of current, the third small flow switching electromagnetic valve 17 works at the left position, the oil inlet B5 is communicated with the first oil outlet A5, the oil outlet B6 is communicated with the second oil outlet A6, and the second multimode brake 23 is not locked; when the coil of the third small flow switching electromagnetic valve 17 is controlled to receive current, the third small flow switching electromagnetic valve 17 works at the right position, the oil inlet B5 is communicated with the second oil outlet A6, the oil outlet B6 is communicated with the first oil outlet A5, and the second multimode brake 23 is reversely locked.
In this embodiment, the hydraulic gear shifting and cooling and lubricating system further includes a parking module including a small flow switching solenoid valve 24 and a parking mechanism 25. The parking mechanism 25 comprises an electromagnetic safety lock 33 and a small-flow switch electromagnetic valve 24 for controlling the parking mechanism 25, an oil inlet B19 of the small-flow switch electromagnetic valve 24 is communicated with the main oil way 100, an oil drain port B20 is connected with an oil return pipeline, and an oil outlet A16 is communicated with a piston cavity of the parking mechanism. When the parking mechanism releases the parking brake, the coil of the electromagnetic safety lock 33 is controlled to receive current, the electromagnetic safety lock 33 is opened, the coil of the small-flow switch electromagnetic valve 24 is controlled to receive current, the small-flow switch electromagnetic valve 24 works at the right position, the oil inlet B19 is communicated with the oil outlet A16, and after the parking mechanism acts to a specified position, the coil of the electromagnetic safety lock 33 is controlled to have no current, the safety lock is locked, and the parking brake release is completed. The parking module adopts the hydraulic solenoid valve 24 and the electromagnetic safety lock 33 to control the action of the parking mechanism in a redundant way, so that the safety and reliability of the parking system are improved.
The oil liquid size circulation control module comprises an overflow valve 10 and a bypass valve 12, wherein the overflow valve 10 is communicated with the cooling and lubricating oil way and an oil inlet of the mechanical pump 3; an oil inlet B25 of the radiator 11 and an oil inlet B18 of the bypass valve 12 are connected in parallel with the bypass valve 12 and the radiator 11 in the cooling and lubricating oil path, and an oil outlet A19 of the radiator 11 is communicated with an oil outlet A15 of the bypass valve 12 and the oil distribution module. Specifically, the first port B17 of the relief valve 10 is communicated with the first oil outlet A1 of the oil pump switching valve 6, the oil outlet a13 of the main pressure regulating mechanical valve 9, the oil inlet B18 of the bypass valve 12, and the oil inlet B25 of the radiator 11, and the second port a14 of the relief valve 10 is communicated with the oil inlet of the mechanical pump 3.
The oil liquid distribution module comprises: three primary cooling lubricating oil distribution restrictors 30, 31, 32, a plurality of secondary cooling lubricating oil distribution restrictors, a plurality of tertiary cooling lubricating oil distribution restrictors; an oil outlet A19 of the radiator 11 is communicated with an oil outlet A15 of the bypass valve 12 and three primary cooling lubricating oil distributing restrictors 30, 31 and 32.
After repeated simulation and test, the bypass valve 12 accurately designs the valve opening pressure, ensures that most of the cooling lubricating oil liquid passes through the bypass valve 12 at low temperature to carry out small circulation, is beneficial to rapid temperature rise of the oil liquid, and controls the temperature of the oil liquid not to exceed the temperature by carrying out external large circulation through the radiator 11 at high temperature. At low temperature, the pressure drop of the radiator 11 and the bypass valve 12 is high, the overflow valve 10 is opened, the control port D4 of the overflow valve 10 pushes the valve core to act under the action of high pressure, the overflow valve 10 works at the left position, the first port B17 is communicated with the second port A14, part of oil returns to the oil suction port of the mechanical pump 3, so that the filtering load of the double-oil-outlet filter screen 2 is reduced, and the radiator 11 is protected from being damaged. The precise design of the primary, secondary and tertiary restrictors for cooling lubricating oil ensures that the oil is sufficient at each cooling and lubricating part of the E-CVT hybrid transmission when the system flows, and reduces the cost of a hydraulic system.
The above embodiments are only for illustrating the technical concept and features of the present invention, and are intended to enable those skilled in the art to understand the present invention and to implement the same, but are not intended to limit the scope of the present invention, and all equivalent changes or modifications made according to the spirit of the present invention should be included in the scope of the present invention.
Claims (4)
1. A hydraulic pressure gear shift and cooling lubrication system for hybrid transmission, characterized by that includes oil feeding system, hydraulic pressure gear shift system and cooling lubrication system, wherein:
the oil supply system comprises a double-oil-outlet filter screen (2), a mechanical pump (3), an electronic pump (4), an oil pump switching valve (6) and a first small-flow switching electromagnetic valve (13) for controlling the oil pump switching valve (6), wherein a first oil outlet of the double-oil-outlet filter screen (2) is communicated with a main oil way through the mechanical pump (3), a second oil outlet of the double-oil-outlet filter screen (2) is communicated with the electronic pump (4), and the electronic pump (4) is communicated with the main oil way or a cooling and lubricating oil way through the oil pump switching valve (6); the oil pump switching valve (6) is provided with a first working position and a second working position, the oil pump switching valve (6) is controlled to work in the first working position or the second working position through the first small flow switching electromagnetic valve (13), when the oil pump switching valve (6) is in the first working position, the oil pump switching valve (6) guides the flow of the electronic pump (4) to the cooling and lubricating oil way, and when the oil pump switching valve (6) is in the second working position, the oil pump switching valve (6) guides the flow of the electronic pump (4) to the main oil way; the hydraulic gear shifting system comprises the main oil way and a gear shifting module; the cooling and lubricating system comprises a heat dissipation module;
an oil outlet of the mechanical pump (3) is communicated with a main oil way, and the flow of the main oil way is led to the hydraulic gear shifting system; an oil outlet of the electronic pump (4) is communicated with an oil inlet (B1) of the oil pump switching valve (6), a first oil outlet (A1) of the oil pump switching valve (6) is communicated with a cooling and lubricating oil circuit, and the flow of the cooling and lubricating oil circuit is led to the cooling and lubricating system; the second oil outlet (A2) of the oil pump switching valve (6) is communicated with the main oil way, the control port D1 of the oil pump switching valve (6) is communicated with the oil outlet (A3) of the first small flow switching electromagnetic valve (13), the oil inlet (B2) of the first small flow switching electromagnetic valve (13) is connected with the main oil way, and the oil outlet (B3) of the first small flow switching electromagnetic valve (13) is connected with an oil return pipeline;
the oil supply system further comprises a first one-way valve (5), a mechanical pump safety valve (7) and a second one-way valve (8); an oil outlet of the mechanical pump (3) is communicated with a main oil way through the second one-way valve (8), and an oil outlet of the electronic pump (4) is communicated with an oil inlet (B1) of the oil pump switching valve (6) through the first one-way valve (5); an oil inlet of the mechanical pump safety valve (7) is communicated with a pipeline between the second one-way valve (8) and an oil outlet of the mechanical pump (3), and the oil outlet of the mechanical pump safety valve (7) is connected with an oil return pipeline;
the hydraulic gear shifting system further comprises a main oil way oil pressure control module, wherein the main oil way oil pressure control module comprises a pressure limiting valve (14) communicated with the main oil way, a first small flow proportional electromagnetic valve (15) communicated with the pressure limiting valve (14), a main pressure regulating mechanical valve (9) communicated with the first small flow proportional electromagnetic valve (15) and an energy accumulator (16); the pressure limiting valve (14) reduces the oil pressure of a main oil way to a certain value and inputs the oil pressure into the first small-flow proportional electromagnetic valve (15), and the valve core opening of the main pressure regulating mechanical valve (9) is controlled through the first small-flow proportional electromagnetic valve (15) so as to control the oil pressure of the main oil way; the accumulator (16) is arranged in a pilot oil path of the main oil path oil pressure control module;
an oil outlet of the pressure limiting valve (14) is communicated with an oil inlet (B11) of the first small-flow proportional electromagnetic valve (15); a first control port (D2) of the main pressure regulating mechanical valve (9) is communicated with the main oil way, a second control port (D3) of the main pressure regulating mechanical valve (9) is communicated with an output port (A9) of the first small flow proportional electromagnetic valve (15), and a valve core of the main pressure regulating mechanical valve (9) enables an oil inlet (B16) of the main pressure regulating mechanical valve (9) to be communicated with oil outlets (A13) at different valve core openings under the action of oil pressures of the first control port D2 and the second control port (D3), so that the oil pressure of the main oil way is ensured to be at a control value; the piston cavity of the energy accumulator (16) is communicated with a second control port (D3) of the main pressure regulating mechanical valve (9) and an output port (A9) of the first small flow proportional electromagnetic valve (15);
the gear shifting module comprises a first clutch (27), a second clutch (29), a first multimode brake (22), a second multimode brake (23), a first high-flow proportional solenoid valve (28) for controlling the first clutch (27), a second high-flow proportional solenoid valve (26) for controlling the second clutch, a first clutch redundancy reversing valve (21), two second low-flow switching solenoid valves (18, 19) for controlling the first multimode brake (22), a first multimode brake redundancy reversing valve (20) and a third low-flow switching solenoid valve (17) for controlling the second multimode brake;
an oil inlet (B13) of the first clutch redundancy reversing valve (21) is communicated with the main oil way, an oil outlet (A10) is communicated with a piston cavity of the first clutch (27) through the second large-flow proportional electromagnetic valve (26), and two control ports (D6, D7) of the first clutch redundancy reversing valve (21) are respectively correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multimode brake (22);
two oil inlets (B14, B15) of the first multi-mode brake redundancy reversing valve (20) are respectively correspondingly communicated with the two second small-flow switching electromagnetic valves (18, 19), and two oil outlets (A11, A12) of the first multi-mode brake redundancy reversing valve (20) are respectively correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multi-mode brake (22); the control port of the first multimode brake redundant reversing valve (20) is communicated with the piston cavity of the first clutch (27);
an oil inlet (B23) of the first large-flow proportional electromagnetic valve (28) is communicated with the main oil way, an oil discharge port (B24) is connected with an oil return pipeline, and an oil outlet (A18) is communicated with a piston cavity of the first clutch (27);
an oil inlet (B21) of the second large-flow proportional electromagnetic valve (26) is communicated with an oil outlet (A10) of the first clutch redundancy reversing valve (21), an oil drain port (B22) is connected with an oil return pipeline, and an oil outlet (A17) is communicated with a piston cavity of the first clutch (27);
an oil inlet (B8) of one second small flow switching electromagnetic valve (18) is communicated with the main oil way, an oil discharge port (B7) is connected with the oil return pipeline, and an oil outlet (A7) is communicated with a first oil inlet (B14) of the first multi-mode brake redundancy reversing valve (20);
an oil inlet (B10) of the other second small flow switching electromagnetic valve (19) is communicated with the main oil way, an oil discharge port (B9) is connected with an oil return pipeline, and an oil outlet (A8) is communicated with a second oil inlet (B15) of the first multi-mode brake redundancy reversing valve (20);
an oil inlet (B5) of the third small flow switching electromagnetic valve (17) is communicated with the main oil way, an oil discharge port (B6) is connected with the oil return pipeline, a first oil outlet (A5) is communicated with a forward locking piston cavity of the second multimode brake (23), and a second oil outlet (A6) is communicated with a reverse locking piston cavity of the second multimode brake (23).
2. A hydraulic shift and cooling lubrication system for a hybrid gearbox according to claim 1, characterized in that it further comprises a parking module comprising a small flow switching solenoid valve (24) and a parking mechanism (25);
the parking mechanism (25) comprises an electromagnetic safety lock (33), an oil inlet (B19) of a small-flow switch electromagnetic valve (24) of the parking mechanism is controlled to be communicated with the main oil way, an oil discharge port (B20) is connected with an oil return pipeline, and an oil outlet (A16) is communicated with a piston cavity of the parking mechanism.
3. The hydraulic shift and cooling lubrication system for a hybrid transmission according to claim 1, wherein the heat dissipation module comprises a radiator (11), the cooling lubrication system further comprising an oil size circulation control module and an oil distribution module;
the oil liquid size circulation control module comprises an overflow valve (10) and a bypass valve (12), and the overflow valve (10) is communicated with the cooling and lubricating oil way and an oil inlet of the mechanical pump (3); an oil inlet (B25) of the radiator (11) and an oil inlet (B18) of the bypass valve (12) are connected in parallel with the radiator (11) in the cooling and lubricating oil path 200, and an oil outlet (A19) of the radiator (11) is communicated with an oil outlet (A15) of the bypass valve (12) and the oil distribution module.
4. A hydraulic shift and cooling lubrication system for a hybrid transmission according to claim 3, wherein the oil distribution module comprises: three primary cooling lubricating oil distribution restrictors (30, 31, 32), a plurality of secondary cooling lubricating oil distribution restrictors, a plurality of tertiary cooling lubricating oil distribution restrictors; an oil outlet (A19) of the radiator (11) is communicated with an oil outlet (A15) of the bypass valve (12) and three primary cooling lubricating oil distributing restrictors (30, 31, 32).
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| CN112879464B (en) * | 2019-11-29 | 2022-09-27 | 上海汽车集团股份有限公司 | Hybrid hydraulic control system and control method |
| CN111271450B (en) * | 2020-01-19 | 2021-02-19 | 东风汽车集团有限公司 | Electro-hydraulic control system and control method for hybrid power transmission |
| CN113757356B (en) * | 2020-06-02 | 2023-07-28 | 广州汽车集团股份有限公司 | Vehicle hydraulic control system and method |
| CN114183486A (en) * | 2020-09-15 | 2022-03-15 | 中联农业机械股份有限公司 | Liquid filling valve group, brake control system and agricultural machine with liquid filling valve group and brake control system |
| CN114235443A (en) * | 2022-02-24 | 2022-03-25 | 南通睿动新能源科技有限公司 | Flow distribution test tool for double-motor hybrid box |
| 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 |
| CN114838119A (en) * | 2022-06-28 | 2022-08-02 | 浙江万里扬新能源驱动有限公司杭州分公司 | Hydraulic control system for hybrid transmission |
| CN116717510A (en) * | 2023-08-10 | 2023-09-08 | 盛瑞传动股份有限公司 | Mixed hydraulic system oil circuit and automatic gearbox |
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