CN211474836U

CN211474836U - Hydraulic gear shifting and cooling and lubricating system for hybrid power transmission

Info

Publication number: CN211474836U
Application number: CN201920932578.9U
Authority: CN
Inventors: 李博; 洪波昌; 何正模
Original assignee: Wuxi Mingheng Hybrid Power Technology Co ltd
Current assignee: Wuxi Mingheng Hybrid Power Technology Co ltd
Priority date: 2019-06-20
Filing date: 2019-06-20
Publication date: 2020-09-11
Anticipated expiration: 2029-06-20

Abstract

The utility model relates to a hybrid transmission technical field discloses a hydraulic pressure shift system and cooling lubrication system for hybrid transmission, and the oil feeding system includes integrated form double oil-out filter screen, mechanical pump, electronic pump, first little flow switch solenoid valve, mechanical pump UNICOM's main oil circuit, and the electronic pump fluid can realize UNICOM's main oil circuit or cold lubrication oil circuit through the control of oil pump diverter valve, realizes 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, and 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 the oil temperature is well controlled, and the cooling and lubricating oil is distributed more accurately. Compared with the prior art, the utility model discloses more be suitable for diesel oil E-CVT hybrid transmission, avoided the double oil pump to rob oily phenomenon, and safe and reliable more when taking place electrical failure.

Description

Hydraulic gear shifting and cooling and lubricating system for hybrid power transmission

Technical Field

The utility model relates to an automatic transmission technical field, in particular to a hydraulic pressure is shifted and cooling and lubricating system for diesel power shunting hybrid transmission (E-CVT).

Background

With the increasing regulations of fuel consumption and emission of automobiles, light commercial vehicles face a severe situation. At present, aiming at the working characteristics of a diesel engine, a hybrid power gearbox adaptive to the diesel engine is developed, and the oil consumption and the emission of a power system can be optimized to the maximum extent. An E-CVT hybrid transmission is a planetary gearset power split device, distinguished from a conventional CVT continuously variable transmission. The hybrid power gearbox adopts an E-CVT framework, and driving comfort can be improved.

The E-CVT hybrid power transmission needs a hydraulic gear shifting system to realize automatic gear shifting when the whole vehicle runs, and each gear shifting is completed through two clutches and two multi-mode brakes which are connected with an engine and a motor in a planet row. The pure electric and hybrid working conditions of the E-CVT hybrid power transmission are 9 forward gears, and in the hybrid power mode, the engine and the motor share the torque requirement of the whole vehicle by controlling the combination and disconnection of different clutches, so that the working range of the engine is adjusted and optimized, the oil consumption and the emission of the system are reduced, and the dynamic property of the system is improved.

The prior art E-CVT hybrid transmissions suffer from a number of drawbacks: for example, a motor, a clutch, a bearing, a planet row and the like of the E-CVT hybrid transmission need cooling lubrication, the cooling lubrication flow needs to be accurately calculated due to the increase of cooling load, an oil supply system in the prior art is not reasonable in design, external pressure drop is large in low-temperature environment, cooling oil excessively passes through external circulation, and the temperature of the oil is slowly increased; for another example, in the prior art, an oil pump of a cooling lubricating oil way and an oil pump of a main oil way of the gearbox can generate an oil robbing phenomenon during working, and the filtering load of an oil outlet filter screen is increased; for example, the mechanical structure of the E-CVT hybrid transmission does not allow the clutch and the multi-mode brake to be closed simultaneously, but when the automobile is in an electrical failure, the clutch and the multi-mode brake of the hydraulic shifting system in the prior art are closed simultaneously, so that the box body is damaged.

Disclosure of Invention

In view of this, the present invention provides a hydraulic shifting and cooling/lubricating system for a hybrid transmission to solve the problems of the prior art.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

the utility model provides a hydraulic pressure is shifted and cooling and lubrication system for hybrid transmission, its characterized in that includes oil feeding system, hydraulic pressure shift system and cooling and 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 switch solenoid 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 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 first small-flow switch electromagnetic valve controls the oil pump switching valve to work at the first working position or the second working position, when the oil pump switching valve is at the first working position, the oil pump switching valve guides the flow of the electronic pump to the cooling lubricating oil path, and when the oil pump switching valve is at the second working position, the oil pump switching valve guides the flow of the electronic pump to the main oil path; 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 preferred 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 guided 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 path, and the flow of the cooling and lubricating oil path is guided to the cooling and lubricating system; the second oil outlet of the oil pump switching valve is communicated with the main oil path, the control port of the oil pump switching valve is communicated with the third oil outlet of the first small-flow switch electromagnetic valve, the oil inlet of the first small-flow switch electromagnetic valve is connected with the main oil path, and the oil outlet of the first small-flow switch electromagnetic valve is connected with the oil return pipeline.

Further preferably, the oil supply system further comprises a first check valve, a mechanical pump relief valve, a second check 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; 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 an oil outlet of the mechanical pump safety valve is connected with an oil return pipeline.

The utility model discloses oil feeding system's two oil-out integrated form filter screens set up two oil-outs, when having guaranteed that one of them oil pump rotational speed rises fast, the phenomenon of robbing oil does not appear in two oil pumps.

Under the hybrid working condition, the mechanical pump provides oil for the main oil way, and the coil current of the first small-flow switch electromagnetic valve is controlled to further control the oil pump switching valve to be in the first working position or the second working position, so that the oil flow direction of the electronic pump is changed according to the system requirements, the flow requirement of the main oil way is guaranteed, and the energy consumption is reduced. Under few working conditions, the mechanical pump can independently bear the oil requirement of the main oil way and the oil requirement of cooling and lubricating oil, and the electronic pump stops working. The first check valve prevents oil from flowing back into the electronic pump. Under the pure electric working condition, the electronic pump works, the mechanical pump does not work, the current of the electromagnetic coil of the first small-flow electromagnetic valve is controlled, the oil pump switching valve is enabled to be in the first working position, and the electronic pump independently bears the pressure flow requirements of the main oil way and the cooling lubricating oil way.

As a preferred technical scheme, the hydraulic gear shifting system further comprises a main oil circuit oil pressure control module, wherein the main oil circuit oil pressure control module comprises a pressure limiting valve communicated with the main oil circuit, a first small flow proportional solenoid valve communicated with the pressure limiting valve, and a main pressure regulating mechanical valve communicated with the first small flow proportional solenoid valve; the pressure limiting valve reduces the oil pressure of the main oil way to a certain value and inputs the oil pressure to the first small-flow proportional solenoid valve, so that the solenoid valve can be prevented from being damaged by overhigh oil pressure; controlling the valve core opening degree of the main pressure regulating mechanical valve through a first small-flow proportional electromagnetic valve so as to control the oil pressure of the main oil way; the accumulator is arranged in a pilot oil way of the main oil way oil pressure control module.

Further preferably, an oil outlet of the pressure limiting valve is communicated with a tenth oil port of the first small flow proportional solenoid valve; a first control port of the main pressure regulating mechanical valve is communicated with the main oil way, a second control port of the main pressure regulating mechanical valve is communicated with an output port of the first small-flow proportional solenoid valve, and a valve core of the main pressure regulating mechanical valve enables a fifteenth oil inlet of the main pressure regulating mechanical valve to be communicated with a twelfth oil outlet at different valve core opening degrees under the action of oil pressures 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 the second control port of the main pressure regulating mechanical valve and the output port of the small-flow electromagnetic proportional valve. The oil inlet of the first small-flow proportional solenoid valve is communicated with the output port at different valve core openings by controlling the current of an electromagnetic coil of the first small-flow proportional solenoid valve, so that the oil pressure of the output port is ensured to be a control value; the valve core of the main pressure regulating mechanical valve enables the oil inlet to be communicated with the oil outlet at different valve core opening degrees under the action of the first control port and the second control port, and the oil pressure of a main oil way is guaranteed to be at a control value. The energy accumulator is arranged on a pilot oil way of the main oil way oil pressure control module, so that oil pressure fluctuation of the system can be relieved, the pressure and cavity requirements of the energy 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 comprises a first clutch, a second clutch, a first multi-mode brake, a second multi-mode brake, a first large flow proportional solenoid valve controlling the first clutch, a second large flow proportional solenoid valve controlling the second clutch, a first clutch redundant directional control valve, a second small flow on-off solenoid valve and a fourth small flow on-off solenoid valve controlling the first multi-mode brake, a first multi-mode brake redundant directional control valve, and a third small flow on-off solenoid valve controlling the second multi-mode brake; a twelfth oil inlet of the first clutch redundant reversing valve is communicated with the main oil path, a ninth oil outlet of the first clutch redundant reversing valve is communicated with a piston cavity of the second clutch through the second large-flow proportional solenoid valve, and two control ports of the first clutch redundant reversing valve are correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multimode brake respectively; a thirteenth oil inlet and a fourteenth oil inlet of the first multi-mode brake redundant reversing valve are respectively and correspondingly communicated with the second small-flow switch electromagnetic valve and the fourth small-flow switch electromagnetic valve, and a tenth oil outlet and an eleventh oil outlet of the first multi-mode brake redundant reversing valve are respectively and correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multi-mode brake; and a control port of the first multi-mode brake redundant reversing valve is communicated with the piston cavity of the second clutch.

Preferably, a twenty-first oil inlet of the first large-flow proportional solenoid valve is communicated with the main oil path, a twenty-second oil outlet of the first large-flow proportional solenoid valve is connected with an oil return pipeline, and a sixteenth oil outlet of the first large-flow proportional solenoid valve is communicated with a piston cavity of the first clutch; a nineteenth oil inlet of the second large-flow proportional solenoid valve is communicated with a ninth oil outlet of the first clutch redundancy reversing valve, a twentieth oil drain port is connected with an oil return pipeline, and a fifteenth oil outlet is communicated with a piston cavity of the second clutch; a seventh oil inlet of the second small-flow switch electromagnetic valve is communicated with the main oil way, a sixth oil drain port is connected with the oil return pipeline, and a seventh oil outlet is communicated with a thirteenth oil inlet of the first multi-mode brake redundant reversing valve; a ninth oil inlet of the fourth small-flow switch solenoid valve is communicated with the main oil way, an eighth oil outlet is connected with an oil return pipeline, and an eighth oil outlet is communicated with a fourteenth oil inlet of the first multi-mode brake redundant reversing valve; and a fourth oil inlet of the third small-flow switch electromagnetic valve is communicated with the main oil way, a fifth oil outlet is connected with the oil return pipeline, a fifth oil outlet is communicated with a forward locking piston cavity of the second multi-mode brake, and a sixth oil outlet is communicated with a reverse locking piston cavity of the second multi-mode brake.

In some preferred embodiments, the hydraulic shifting and cooling lubrication system further comprises a parking module comprising a low flow on-off solenoid valve and a parking mechanism; the parking mechanism comprises an electromagnetic safety lock, a seventeenth oil inlet of a small-flow switch electromagnetic valve of the parking mechanism is controlled to be communicated with the main oil way, an eighteenth oil drain port is connected with an oil return pipeline, and a fourteenth 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 lubricating 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; a twenty-third oil inlet of the radiator and a sixteenth oil inlet of the bypass valve are connected in parallel with the radiator in the cooling and lubricating oil path, and a seventeenth oil outlet of the radiator is communicated with a thirteenth 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 includes: three first-stage cooling lubricating oil distribution flow restrictors, a plurality of second-stage cooling lubricating oil distribution flow restrictors and a plurality of third-stage cooling lubricating oil distribution flow restrictors; and a seventeenth oil outlet of the radiator is communicated with a thirteenth oil outlet of the bypass valve and the three first-stage cooling lubricating oil distribution flow restrictors.

The bypass valve accurate design valve opening pressure guarantees that the cooling lubrication fluid is mostly through the bypass valve when low temperature, carries out the microcirculation, does benefit to fluid rapid heating up, and during high temperature, the cooling lubrication fluid passes through the radiator, carries out outside major cycle, and the control fluid temperature is not overtemperature. At low temperature, the pressure drop of the radiator and the bypass valve is high, the overflow valve is opened to protect the radiator, and part of oil flows back to the oil pumping port of the mechanical pump. A plurality of first-stage, second-stage and third-stage flow restrictors for cooling lubricating oil are accurately designed, so that sufficient oil is ensured at each cooling lubricating part of the E-CVT hybrid power transmission in the system flow.

Due to the adoption of the technical scheme, the utility model discloses following beneficial effect is reached.

The utility model provides an oil feeding system is applied to E-CVT hybrid transmission hydraulic system's fluid and supplies with, satisfies the flow and the pressure demand of the whole case of each gear, has reduced hydraulic system's energy consumption, has solved the problem that the oily was robbed to the double oil pump during operation, and overflow fluid gets into the oil pump oil absorption mouth, has reduced the filtration load of filter screen.

The utility model provides a hydraulic pressure gear shift system is applied to E-CVT hybrid transmission gear control, can realize that 9 gears are smooth-going, adjusts the work interval of engine on a large scale, reduces whole car oil consumption and discharges. Meanwhile, the mechanical structure of the E-CVT hybrid power transmission does not allow the clutch and the multi-mode brake to be closed simultaneously, and the redundant reversing valve performs double protection on a hydraulic system, so that the damage to a box body due to the fact that the clutch and the multi-mode brake are combined simultaneously due to electrical faults is avoided.

The utility model provides a cooling and lubrication system is applied to the cooling and lubrication control of E-CVT hybrid transmission, through several one-level, second grade, the accurate design of tertiary current limiter to the cooling and lubrication fluid for the flow supplies with more accurately. The bypass valve and the radiator enable oil in the gearbox to be heated up quickly at low temperature, and oil temperature can be better controlled without exceeding the limit at high temperature. The overflow valve protects the radiator from overpressure damage.

The utility model provides a hydraulic pressure is shifted and cooling and lubrication system for hybrid transmission is to a great deal of problem and defect that exist among the prior art, reasonable in design's branch oil orifice, increase the bypass valve simultaneously before dividing the oil circuit, parallelly connected with the radiator outside the box, outside pressure drop when can reducing low temperature, when ambient temperature is lower has been solved simultaneously, cooling fluid is too much through the extrinsic cycle, the slow problem of fluid intensification, be particularly useful for diesel oil E-CVT hybrid transmission, extensive application prospect and huge commercial value have.

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 invention will be further described with reference to examples of embodiments shown in the drawings.

As shown in fig. 1, the hydraulic shifting and cooling-lubricating system for the hybrid transmission according to the embodiment is characterized by comprising an oil supply system, a hydraulic shifting system and a cooling-lubricating system. The hydraulic gear shifting system comprises the 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 liquid size circulation control module and an oil liquid distribution module, wherein the heat dissipation module comprises a radiator 11.

The oil supply system supplies flow and pressure to the whole oil pressure system of the E-CVT hybrid power gearbox. 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 switch 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 100 through the mechanical pump 3 through 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 a first oil inlet B1 of the oil pump switching valve 6 through the first one-way valve. 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 an oil outlet of the mechanical pump safety valve 7 is connected with an oil return pipeline.

An 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 guided to the hydraulic gear shifting system; an oil outlet of the electronic pump 4 is communicated with a first oil inlet B1 of the oil pump switching valve 6. The oil pump switching valve 6 has a first working position and a second working position, and the first small flow switch solenoid valve 13 controls the oil pump switching valve 6 to work at the first working position or the second working position. When the oil pump switching valve 6 is in the first working position, the first 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 guides the flow of the electronic pump 4 to the cooling and lubricating oil path 200. When the oil pump switching valve 6 is in the second working position, the first 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 third oil outlet A3 of the first small flow switch solenoid valve 13, the first oil inlet B1 of the first small flow switch solenoid valve 13 is connected with the main oil path 100, and the third oil outlet B3 of the first small flow switch solenoid valve 13 is connected with an oil return pipeline.

The main oil way oil pressure control module comprises a pressure limiting valve 14 communicated with the main oil way 100, a first small flow proportional solenoid valve 15 communicated with the pressure limiting valve 14, and a main pressure regulating mechanical valve 9 communicated with the first small flow proportional solenoid valve 15; an oil inlet of the pressure limiting valve 14 is communicated with the main oil way 100, a fourth oil outlet A4 of the pressure limiting valve 14 is communicated with a tenth oil port B11 of the first small flow rate proportional solenoid valve 15, and an eleventh oil outlet B12 of the first small flow rate proportional solenoid valve 15 is connected with an oil return pipeline. The first control port D2 of the main pressure-regulating mechanical 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 the embodiment, the mechanical pump 3 and the electronic pump 4 respectively or simultaneously work according to different working condition requirements of the system, in a pure electric working condition, only the electronic pump 4 works, oil supplied by the electronic pump 4 is communicated with the first oil inlet B1 of the oil pump switching valve 6 through the check valve 5, the first oil inlet B1 of the oil pump switching valve 6 is communicated with the second oil outlet a2, and the second oil outlet a2 is connected with the main oil way 100 to complete pressure establishment of the main oil way; the fifteenth oil inlet B16 of the main pressure regulating mechanical valve 9 is communicated with the main oil path 100, the fifteenth oil inlet B16 and the twelfth oil outlet A13 are communicated with a certain valve core opening degree under the oil pressure action of the first control port D2 and the second control port D3 of the main pressure regulating mechanical valve 9, and oil is led to the cooling lubricating oil path 200. When the hybrid power is in a working condition, the mechanical pump 3 works, the electronic pump 4 can work or does not work according to the flow demand of a hydraulic system, the electronic pump 4 changes the output flow by adjusting the rotating speed of an oil pump motor (EM motor) when working, if the flow supplied to the main oil way 100 by the mechanical pump 3 meets the pressure building demand, the current of an electromagnetic coil of the first small-flow switch electromagnetic valve 13 is controlled, the second oil inlet B2 of the first small-flow switch electromagnetic valve 13 is communicated with the third oil outlet A3, the control port D1 of the oil pump switching valve 6 is communicated with the third oil outlet A3 of the first small-flow switch electromagnetic valve 13, the oil pressure of the control port D1 enables a valve core of the oil pump switching valve 6 to act, the first 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; when the mechanical pump 3 and the electronic pump 4 work simultaneously, the working conditions that the rotating speed rises suddenly are generated, and the double oil outlets of the integrated double-oil-outlet filter screen 2 solve the problem that the mechanical pump 3 and the electronic pump 4 mutually rob oil under the working conditions.

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 solenoid valve 15, so that the first small flow rate proportional solenoid valve 15 can be prevented from being damaged by overhigh oil pressure; the spool 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 action of the oil pressures of the first control port D2 and the second control port D3, the valve core of the main pressure regulating mechanical valve 9 enables a fifteenth oil inlet B16 of the main pressure regulating mechanical valve 9 to be communicated with a twelfth oil outlet a13 at different valve core openings, so as to ensure that the oil pressure of a main oil path is at a control value; the piston chamber 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 rate proportional solenoid valve 15.

By controlling the current of the solenoid coil of the first small flow rate proportional solenoid valve 15, the tenth oil port B11 of the first small flow rate proportional solenoid valve 15 is communicated with the different valve core opening degrees of the output port a9, 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, a valve core of the main pressure regulating mechanical valve 9 enables a fifteenth oil inlet B16 to be communicated with a twelfth oil outlet A13 in different valve core opening degrees, and the oil pressure of a main oil way 100 is guaranteed to be at a control value. The energy accumulator 16 is arranged on a pilot oil way of the main oil way oil pressure control module, so that oil pressure fluctuation of the system can be relieved, the pressure and cavity requirements of the energy accumulator 16 are reduced, and the arrangement space of the whole hydraulic system is saved.

The hydraulic shifting system controls gear control of the E-CVT hybrid transmission. As shown in fig. 1 and 2, the shift modules in the hydraulic shift system include a C0 clutch, a C1 clutch 29, a BE1 multimode brake 22 and a BE2 multimode brake 23, where for ease of differentiation, the CO clutch is the second clutch 27, the C1 clutch is the first clutch 29, the BE1 multimode brake is the first multimode brake 22, and the BE2 multimode brake is the second multimode brake 23.

The shifting module also comprises a first large flow proportional solenoid valve 28 controlling the first clutch 29, a second large flow proportional solenoid valve 26 controlling the second clutch, a first clutch redundancy directional valve 21, a second small flow on-off solenoid valve 18 and a fourth small flow on-off solenoid valve 19 controlling the first multi-mode brake 22, a first multi-mode brake redundancy directional valve 20, and a third small flow on-off solenoid valve 17 controlling the second multi-mode brake 23. The specific connection of the components is described in detail below.

The twenty-first oil inlet B23 of the first large-flow proportional solenoid valve 28 is communicated with the main oil path 100, the twenty-second oil outlet B24 is connected with an oil return pipeline, and the sixteenth oil outlet A18 is communicated with a piston cavity of the first clutch 29.

A nineteenth oil inlet B21 of the second large-flow proportional solenoid valve 26 is communicated with a ninth oil outlet A10 of the first clutch redundant directional control valve 21, a twentieth oil outlet B22 is connected with an oil return pipeline, and a fifteenth oil outlet A17 is communicated with a piston cavity of the second clutch 27.

A twelfth oil inlet B13 of the first clutch redundancy reversing valve 21 is communicated with the main oil path 100, a ninth oil outlet A10 is communicated with a piston cavity of the second clutch 27 through a second large-flow proportional solenoid valve 26, and two control ports D6 and D7 of the first clutch redundancy reversing valve 21 are respectively and correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multimode brake 22.

The thirteenth oil inlet B14 and the fourteenth oil inlet B15 of the first multi-mode brake redundant reversing valve 20 are respectively communicated with the second small flow switch solenoid valve 18 and the fourth small flow switch solenoid valve 19, and the tenth oil outlet A11 and the eleventh oil outlet 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 multi-mode brake redundant directional control valve 20 is in communication with the piston chamber of the second clutch 27.

The seventh oil inlet B8 of the second small-flow switch solenoid valve 18 is communicated with the main oil path 100, the sixth oil outlet B7 is connected with an oil return pipeline, and the seventh oil outlet A7 is communicated with the thirteenth oil inlet B14 of the first multi-mode brake redundant reversing valve 20.

The ninth oil inlet B10 of the fourth small flow switch solenoid valve 19 is communicated with the main oil path 100, the eighth oil outlet B9 is connected with an oil return pipeline, and the eighth oil outlet A8 is communicated with the fourteenth oil inlet B15 of the first multi-mode brake redundant directional control valve 20.

A fourth oil inlet B5 of the third small-flow switch electromagnetic valve 17 is communicated with the main oil path 100, a fifth oil outlet B6 is connected with an oil return pipeline, a fifth oil outlet A5 is communicated with a forward locking piston cavity of the second multi-mode brake 23, and a sixth oil outlet A6 is communicated with a reverse locking piston cavity of the second multi-mode brake 23.

When the first multimode brake 22 is in a non-locking action, the seventh oil inlet B8 port of the second small flow switch solenoid valve 18 is communicated with the seventh oil outlet a7, the oil inlet B9 of the fourth small flow switch solenoid valve 19 is communicated with the eighth oil outlet A8, at this time, the first clutch redundancy reversing valve 21 works in the middle position, the twelfth oil inlet B13 is communicated with the ninth oil outlet a10, that is, the main oil path 100 is communicated with the nineteenth oil inlet B21 of the second large flow proportional solenoid valve 26, the coil current of the second large flow proportional solenoid valve 26 is controlled, the nineteenth oil inlet B21 is communicated with the fifteenth oil outlet a17, the fifteenth oil outlet a17 reaches the control pressure, and the second clutch 27 completes a combining action. When the first multi-mode brake 22 is locked clockwise, the seventh oil inlet B8 of the second small flow switch solenoid valve 18 is communicated with the seventh oil outlet a7, the oil inlet B9 of the fourth small flow switch solenoid valve 19 is communicated with the eighth oil outlet A8, at this time, the control port D7 of the first clutch redundant directional control valve 21 is the same as the forward locking piston cavity oil pressure of the first multi-mode brake 22, the spool moves, the first clutch redundant directional control valve 21 works at the right position, the twelfth oil inlet B13 and the ninth oil outlet a10 are cut off, the oil in the main oil path 100 cannot be communicated to the nineteenth oil inlet B21 of the second large flow proportional solenoid valve 26, and even if the coil of the second large flow proportional solenoid valve 26 receives current, the second clutch 27 cannot be closed.

When the first multi-mode brake 22 is locked, the coil of the second large-flow proportional solenoid valve 26 may receive current due to a fault of an HCU (Hybrid Control Unit) or electromagnetic interference, and the second clutch 27 is closed, so that the transmission is damaged. Therefore, the utility model discloses avoid the emergence of this trouble effectively, improved E-CVT hybrid transmission's security and reliability.

When the second clutch 27 is not closed, the coil of the second large-flow proportional solenoid valve 26 has no current, the second large-flow proportional solenoid valve 26 works at the left position, the fifteenth oil outlet a17 is communicated with the twentieth oil outlet B22 to be connected with an oil return pipeline, the control port D5 of the first multi-mode brake redundant directional control valve 20 is communicated with the fifteenth oil outlet a17, the control port D5 has no oil pressure, the first multi-mode brake redundant directional control valve 20 works at the right position, the thirteenth oil inlet B14 is communicated with the tenth oil outlet a11, and the fourteenth oil inlet B15 is communicated with the eleventh oil outlet a 12; if the electromagnetic coil of the fourth small flow switch electromagnetic valve 19 receives current, the ninth oil inlet B10 is communicated with the eighth oil outlet A8, and the first multi-mode brake 22 is reversely locked; if the electromagnetic coil of the second small flow switch electromagnetic valve 18 receives current, the seventh oil inlet B8 of the second small flow switch electromagnetic valve 18 is communicated with the seventh oil outlet A7, and the first multi-mode brake 22 is positively locked.

When the first clutch is closed, a coil of the second large-flow proportional solenoid valve 26 receives current, the second large-flow proportional solenoid valve 26 works at the right position, a fifteenth oil outlet A17 is communicated with a nineteenth oil inlet B21, a control port D5 of the first multi-mode brake redundant reversing valve 20 is communicated with a fifteenth oil outlet A17, the oil pressure of the control port D5 pushes a valve core, the first multi-mode brake redundant reversing valve 20 works at the left position, a thirteenth oil inlet B14 is cut off from a tenth oil outlet A11, and a fourteenth oil inlet B15 is cut off from an eleventh oil outlet A12; at this time, the first multi-mode brake 22 is not locked in the forward or reverse direction regardless of whether the solenoid coil of the second small flow rate switching solenoid valve 18 or the solenoid coil of the fourth small flow rate switching solenoid valve 19 receives a current due to an HCU failure or electromagnetic interference. Therefore, the utility model discloses avoided second clutch 27 and first multimode brake 22 to appear the closed trouble simultaneously because of HCU trouble or electromagnetic interference, improved E-CVT hybrid transmission's reliability and security.

The twenty-first oil inlet B23 of the first large-flow proportional solenoid valve 28 for controlling the first clutch 29 is communicated with the main oil circuit 100, the twenty-second oil drain B24 is connected with an oil return pipeline, the sixteenth oil outlet A18 is communicated with a piston cavity of the first clutch 29, a coil of the first large-flow proportional solenoid valve 28 is controlled to receive current, the first large-flow proportional solenoid valve 28 works at the right position, the twenty-first oil inlet B23 is communicated with the sixteenth oil outlet A18, and the first clutch 29 is closed.

A fourth oil inlet B5 of a third small-flow switch electromagnetic valve 17 for controlling the second multi-mode brake 23 is communicated with a main oil path 100, a fifth oil drain port B6 is connected with an oil return pipeline, a fifth oil outlet A5 is communicated with a non-locking piston cavity of the second multi-mode brake 23, and a sixth oil outlet A6 is communicated with a reverse locking piston cavity of the second multi-mode brake 23. When the coil of the third small flow switch solenoid valve 17 is controlled to be free of current, the third small flow switch solenoid valve 17 works at the left position, the fourth oil inlet B5 is communicated with the fifth oil outlet A5, the fifth oil outlet B6 is communicated with the sixth oil outlet A6, and the second multimode brake 23 is unlocked; when the coil of the third small flow switch electromagnetic valve 17 is controlled to receive current, the third small flow switch electromagnetic valve 17 works at the right position, the fourth oil inlet B5 is communicated with the sixth oil outlet a6, the fifth oil outlet B6 is communicated with the fifth oil outlet a5, and the second multimode brake 23 is locked reversely.

In this embodiment, the hydraulic shifting and cooling-lubricating system further includes a parking module, and the parking module includes a small flow switch solenoid valve 24 and a parking mechanism 25. The parking mechanism 25 comprises an electromagnetic safety lock 33 and a small-flow switch solenoid valve 24 for controlling the parking mechanism 25, a seventeenth oil inlet B19 of the small-flow switch solenoid valve 24 is communicated with a main oil path 100, an eighteenth oil outlet B20 is connected with an oil return pipeline, and a fourteenth oil outlet A16 is communicated with a piston cavity of the parking mechanism. When the parking brake of the parking mechanism is released, 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 seventeenth oil inlet B19 is communicated with the fourteenth oil outlet A16, after the parking mechanism moves to the appointed 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 utility model discloses a parking module adopts hydraulic pressure solenoid valve 24 and the action of the 33 redundant control parking mechanisms of electromagnetism safety lock, has improved parking system's security and reliability.

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; a twenty-third oil discharge port B25 of the radiator 11 and a sixteenth oil inlet B18 of the bypass valve 12, the bypass valve 12 and the radiator 11 are connected in parallel in the cooling lubricating oil path, and a seventeenth oil outlet a19 of the radiator 11 is communicated with a thirteenth oil outlet a15 of the bypass valve 12 and the oil distribution module. Specifically, the first port B17 of the overflow valve 10 is communicated with the first oil outlet a1 of the oil pump switching valve 6, the twelfth oil outlet a13 of the main pressure regulating mechanical valve 9, the sixteenth oil inlet B18 of the bypass valve 12, and the twenty-third oil outlet B25 of the radiator 11, and the second port a14 of the overflow valve 10 is communicated with the oil inlet of the mechanical pump 3.

The oil distribution module includes: three primary cooling lubricant

distribution flow restrictors

30, 31, 32, a plurality of secondary cooling lubricant distribution flow restrictors, and a plurality of tertiary cooling lubricant distribution flow restrictors; the seventeenth oil outlet A19 of the radiator 11 is communicated with the thirteenth oil outlet A15 of the bypass valve 12 and the three first-stage cooling lubricating oil distributing

flow 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 passes through the bypass valve 12 at low temperature to perform small circulation, is beneficial to quick temperature rise of the oil, and performs external large circulation when the cooling lubricating oil passes through the radiator 11 at high temperature to control the temperature of the oil not to exceed the 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, and part of oil flows back 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 accurate design of a plurality of first-level, second-level and third-level flow restrictors for cooling lubricating oil ensures that the oil in each cooling lubricating part of the E-CVT hybrid power transmission is sufficient when the system flow is ensured, and the cost of a hydraulic system is reduced.

The above embodiments are only for illustrating the technical concept and features of the present invention, and the purpose of the embodiments is to enable people skilled in the art to understand the contents of the present invention and to implement the present invention, which cannot limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered by the protection scope of the present invention.

Claims

1. The utility model provides a hydraulic pressure is shifted and cooling and lubrication system for hybrid transmission, its characterized in that includes oil feeding system, hydraulic pressure shift system and cooling and 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 switch solenoid 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 first small-flow switch electromagnetic valve (13) is used for controlling the oil pump switching valve (6) to work at the first working position or the second working position, when the oil pump switching valve (6) is at the first working position, the oil pump switching valve (6) guides the flow of the electronic pump (4) to the cooling lubricating oil path, and when the oil pump switching valve (6) is at the second working position, the oil pump switching valve (6) guides the flow of the electronic pump (4) to the main oil path; 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.

2. A hydraulic shifting and cooling lubrication system for a hybrid transmission according to claim 1, characterised in that the oil outlet of the mechanical pump (3) is in communication with a main oil circuit, the flow of which is directed to the hydraulic shifting system; an oil outlet of the electronic pump (4) is communicated with a first 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 path, and the flow of the cooling and lubricating oil path is guided 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 third oil outlet (A3) of the first small flow switch electromagnetic valve (13), the first oil inlet (B1) of the first small flow switch electromagnetic valve (13) is connected with the main oil way, and the third oil outlet (B3) of the first small flow switch electromagnetic valve (13) is connected with the oil return pipeline.

3. A hydraulic shifting and cooling lubrication system for a hybrid transmission according to claim 2, wherein said oil supply system further comprises a first check valve (5), a mechanical pump relief valve (7), a second check 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 a first 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 an oil outlet of the mechanical pump safety valve (7) is connected with an oil return pipeline.

4. A hydraulic shifting and cooling lubrication system for a hybrid transmission as defined in claim 1 wherein: the hydraulic gear shifting system further comprises a main oil circuit oil pressure control module, wherein the main oil circuit oil pressure control module comprises a pressure limiting valve (14) communicated with the main oil circuit, a first small flow proportional solenoid valve (15) communicated with the pressure limiting valve (14), a main pressure regulating mechanical valve (9) communicated with the first small flow proportional solenoid 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 then inputs the oil pressure into the first small-flow proportional solenoid valve (15), and the valve core opening of the main pressure regulating mechanical valve (9) is controlled through the first small-flow proportional solenoid 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.

5. The hydraulic shifting and cooling lubrication system for a hybrid transmission as recited in claim 4, wherein: an oil outlet of the pressure limiting valve (14) is communicated with a tenth oil port (B11) of the first small flow rate proportional solenoid 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 rate proportional solenoid valve (15), and a valve core of the main pressure regulating mechanical valve (9) is communicated with a fifteenth oil inlet (B16) and a twelfth oil outlet (A13) at different valve core opening degrees under the oil pressure action of the first control port (D2) and the second control port (D3) so as to ensure that the oil pressure of the main oil way is at a control value; and a piston cavity of the 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 solenoid valve (15).

6. A hydraulic shifting and cooling lubrication system for a hybrid transmission according to any one of claims 1 to 5, wherein: the gear shifting module comprises a first clutch (29), a second clutch (27), a first multi-mode brake (22), a second multi-mode brake (23), a first large flow proportional solenoid valve (28) for controlling the first clutch (29), a second large flow proportional solenoid valve (26) for controlling the second clutch (27), a first clutch redundancy reversing valve (21), a second small flow switch solenoid valve (18) and a fourth small flow switch solenoid valve (19) for controlling the first multi-mode brake (22), a first multi-mode brake redundancy reversing valve (20), and a third small flow switch solenoid valve (17) for controlling the second multi-mode brake;

a twelfth oil inlet (B13) of the first clutch redundancy reversing valve (21) is communicated with the main oil path, a ninth oil outlet (A10) is communicated with a piston cavity of the second clutch (27) through the second large-flow proportional electromagnetic valve (26), and two control ports (D6 and D7) of the first clutch redundancy reversing valve (21) are respectively and correspondingly communicated with a forward locking piston cavity and a reverse locking piston cavity of the first multimode brake (22);

a thirteenth oil inlet (B14) and a fourteenth oil inlet (B15) of the first multi-mode brake redundant reversing valve (20) are respectively and correspondingly communicated with the second small-flow switch electromagnetic valve (18) and the fourth small-flow switch electromagnetic valve (19), and a tenth oil outlet A11 and an eleventh oil outlet A12 of the first multi-mode brake redundant reversing valve (20) are respectively and 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 multi-mode brake redundant directional control valve (20) is in communication with the piston chamber of the second clutch (27).

7. The hydraulic shifting and cooling lubrication system for a hybrid transmission as recited in claim 6, wherein: a twenty-first oil inlet (B23) of the first large-flow proportional solenoid valve (28) is communicated with the main oil way, a twenty-second oil outlet (B24) is connected with an oil return pipeline, and a sixteenth oil outlet (A18) is communicated with a piston cavity of the first clutch (29);

a nineteenth oil inlet (B21) of the second large-flow proportional solenoid valve (26) is communicated with a ninth oil outlet (A10) of the first clutch redundancy reversing valve (21), a twentieth oil outlet (B22) is connected with an oil return pipeline, and a fifteenth oil outlet (A17) is communicated with a piston cavity of the second clutch (27);

a seventh oil inlet (B8) of the second small-flow switch solenoid valve (18) is communicated with the main oil way, a sixth oil drain port (B7) is connected with the oil return pipeline, and a seventh oil outlet (A7) is communicated with a thirteenth oil inlet (B14) of the first multi-mode brake redundant reversing valve (20);

a ninth oil inlet (B10) of the fourth small-flow switch electromagnetic valve (19) is communicated with the main oil way, an eighth oil drain port (B9) is connected with an oil return pipeline, and an eighth oil outlet (A8) is communicated with a fourteenth oil inlet (B15) of the first multi-mode brake redundant reversing valve (20);

and a fourth oil inlet (B5) of the third small-flow switch solenoid valve (17) is communicated with the main oil way, a fifth oil drain port (B6) is connected with the oil return pipeline, a fifth oil outlet (A5) is communicated with a forward locking piston cavity of the second multi-mode brake (23), and a sixth oil outlet (A6) is communicated with a reverse locking piston cavity of the second multi-mode brake (23).

8. The hydraulic shifting and cooling lubrication system for a hybrid transmission according to any one of claims 1-5, further comprising a parking module comprising a small flow on-off solenoid valve (24) and a parking mechanism (25);

parking mechanism (25) include electromagnetic safety lock (33), control parking mechanism's seventeenth oil inlet (B19) of low flow switch solenoid valve (24) with main oil circuit UNICOM, eighteenth oil drain port (B20) are connected back oil pipe way, fourteenth oil-out (A16) with parking mechanism's piston chamber UNICOM.

9. The hydraulic shifting and cooling-lubricating system for the hybrid power transmission according to any one of claims 1-5, characterized in that the heat dissipation module comprises a radiator (11), and the cooling-lubricating 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 (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); a twenty-third oil discharge port (B25) of the radiator (11) and a sixteenth oil inlet (B18) of the bypass valve (12), the bypass valve (12) and the radiator (11) are connected in parallel in the cooling and lubricating oil path (200), and a seventeenth oil discharge port (A19) of the radiator (11) is communicated with a thirteenth oil discharge port (A15) of the bypass valve (12) and the oil distribution module.

10. The hydraulic shifting and cooling lubrication system for a hybrid transmission as recited in claim 9, wherein said oil distribution module comprises: three primary cooling lubricant distribution flow restrictors (30, 31, 32), a plurality of secondary cooling lubricant distribution flow restrictors, and a plurality of tertiary cooling lubricant distribution flow restrictors; the seventeenth oil outlet (A19) of the radiator (11) is communicated with the thirteenth oil outlet (A15) of the bypass valve (12) and the three primary cooling lubricating oil distributing flow restrictors (30, 31, 32).