Hydraulic device, hydraulic control system, vehicle and control method

Abstract

The present invention relates to a hydraulic device, a hydraulic control system, a vehicle and a control method. The hydraulic device comprises a cooling and lubricating oil circuit and a pressure control oil circuit, wherein the cooling and lubricating oil circuit comprises a first oil tank, a first oil pump and a first oil circuit, the first oil tank being configured to supply oil to the first oil pump, and the first oil pump being configured to provide hydraulic oil for the first oil circuit, so as to cool and lubricate an electromechanical coupling transmission by means of the first oil circuit; the pressure control oil circuit comprises a second oil tank, a second oil pump and a second oil circuit, the second oil tank being configured to supply oil to the second oil pump, and the second oil pump being configured to provide hydraulic oil for the second oil circuit, so as to control the engagement and disengagement of a clutch of the electromechanical coupling transmission by means of the second oil circuit; and a first throttle valve is provided on the second oil circuit and configured to control the amount of oil supplemented to the second oil tank from the first oil circuit. The hydraulic device of the present invention realizes the efficient utilization of hydraulic oil.

Description

Hydraulic device, hydraulic control system, vehicle and control method

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to the Chinese patent application filed with the Patent Office of China on March 6, 2024, with application number 202410255853.3 and patent application name “Hydraulic device, hydraulic control system, vehicle and control method”, and the Chinese patent application filed with the Patent Office of China on March 6, 2024, with application number 202420436778.6 and patent application name “Hydraulic device, hydraulic control system and vehicle”, all contents of which are incorporated by reference into this application. Technical Field

[0003] The present invention belongs to the technical field of vehicle bodies, and in particular relates to a hydraulic device, a hydraulic control system, a vehicle and a control method. Background Art

[0004] The electromechanical transmission is a key component of hybrid electric vehicles (HEVs). Its high reliability, low cost, and high transmission efficiency are essential for achieving optimal cost-performance. The hydraulic control system is a key subsystem of the HEV, and its performance directly impacts overall transmission performance. The hydraulic control system controls mode switching, motor cooling, and shaft gear lubrication in HEVs.

[0005] At present, the pressure control oil circuit (high-pressure oil circuit) and the cooling and lubricating oil circuit (low-pressure oil circuit) of the hydraulic control system of a common electromechanical coupling transmission are supplied by different oil tanks, and the two oil tanks are independent of each other. The excess hydraulic oil in the first oil circuit directly flows back to the first oil tank and cannot be replenished to the second oil tank, resulting in the hydraulic oil in the oil tank of the cooling and lubricating oil circuit of the hydraulic control system cannot be efficiently utilized. Summary of the Invention

[0006] The technical problem to be solved by the present invention is: to provide a hydraulic device, a hydraulic control system, a vehicle and a control method to address the problem that the hydraulic oil in the oil tank of the cooling and lubricating oil circuit of the hydraulic control system of the existing electromechanical coupling transmission cannot be efficiently utilized.

[0007] To solve the above technical problems, on the one hand, an embodiment of the present invention provides a hydraulic device, a hydraulic device including a cooling lubricating oil circuit and a pressure control oil circuit;

[0008] The cooling and lubricating oil circuit includes a first oil tank, a first oil pump, and a first oil circuit. The first oil pump is connected between the first oil tank and the first oil circuit. The first oil tank is used to supply oil to the first oil pump. The first oil pump is used to provide hydraulic oil to the first oil circuit to cool and lubricate the electromechanical coupling transmission through the first oil circuit.

[0009] The pressure control oil circuit includes a second oil tank, a second oil pump, and a second oil circuit. The second oil pump is connected between the second oil tank and the second oil circuit. The second oil tank is used to supply oil to the second oil pump. The second oil pump is used to provide hydraulic oil to the second oil circuit to control the engagement and disengagement of the clutch of the electromechanical coupling transmission through the second oil circuit.

[0010] The second oil circuit is provided with a first throttle valve, which is connected between the first oil circuit and the second oil tank and is used to control the amount of oil supplied from the first oil circuit to the second oil tank.

[0011] In the hydraulic device according to an embodiment of the present invention, a first throttle valve is disposed between the first oil circuit of the cooling and lubricating oil circuit (low-pressure oil circuit) and the second oil tank of the pressure control oil circuit (high-pressure oil circuit). The first throttle valve is used to control the amount of oil supplied from the first oil circuit to the second oil tank. This allows excess hydraulic oil in the cooling and lubricating oil circuit to flow not directly back to the first oil tank of the cooling and lubricating oil circuit, but instead to be supplied to the second oil tank for use in the pressure control oil circuit to control clutch pressure, achieving efficient utilization of the hydraulic oil.

[0012] Optionally, the first fuel tank is provided independently of the second fuel tank.

[0013] Optionally, the first oil tank is connected to the second oil tank through an overflow pipe, so that the hydraulic oil overflowing from the second oil tank can flow back to the first oil tank.

[0014] Optionally, a first solenoid valve is provided in the first oil circuit, and the inlet of the first oil pump is connected to the first oil tank; the cooling oil circuit of the electromechanical coupling transmission includes a drive motor cooling oil circuit, a clutch cooling oil circuit, and a generator cooling oil circuit, and the second oil circuit is connected to the clutch cooling oil circuit and the drive motor cooling oil circuit;

[0015] The first solenoid valve is connected between the outlet of the first oil pump and the generator cooling oil circuit and the clutch cooling oil circuit, and is used to control the on / off supply of oil from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve.

[0016] Optionally, the first solenoid valve is a three-position four-way valve, and the valve core of the first solenoid valve can slide and switch between a first position, a second position and a third position;

[0017] When the valve core of the first solenoid valve is in the first position, the hydraulic oil in the first oil circuit flows into the clutch cooling oil circuit and the generator cooling oil circuit respectively through the first solenoid valve;

[0018] When the valve core of the first solenoid valve is in the second position, the hydraulic oil in the first oil circuit flows into the generator cooling oil circuit only through the first solenoid valve;

[0019] When the valve core of the first solenoid valve is in the third position, the hydraulic oil in the first oil circuit is cut off at the first solenoid valve.

[0020] Optionally, the first inlet and the second inlet of the first solenoid valve are connected to the outlet of the first oil pump through a first pipeline, the first inlet and the second inlet of the first solenoid valve are connected to the first oil tank and the inlet of the first oil pump through a second pipeline, the first pipeline is connected to the clutch cooling oil circuit through a third pipeline, the connection point of the first pipeline and the third pipeline is located between the outlet of the first oil pump and the first inlet of the first solenoid valve, and the second pipeline is connected to the drive motor cooling oil circuit through a fourth pipeline;

[0021] The first outlet of the first solenoid valve is connected to the third pipeline through a fifth pipeline, and the second outlet of the first solenoid valve is connected to the generator cooling oil circuit through a sixth pipeline;

[0022] When the valve core of the first solenoid valve is in the first position, the first inlet is connected to the first outlet, and the second inlet is connected to the second outlet;

[0023] When the valve core of the first solenoid valve is in the second position, the first inlet is blocked from the first outlet, and the second inlet is connected to the second outlet;

[0024] When the valve core of the first solenoid valve is located at the third position, the first inlet is blocked from the first outlet, and the second inlet is blocked from the second outlet.

[0025] Optionally, a second throttle valve is provided on the fourth pipeline, and the second throttle valve is used to control the amount of oil flowing from the fourth pipeline into the drive motor cooling oil circuit;

[0026] The sixth pipeline is provided with a third throttle valve, and the third throttle valve is used to control the amount of oil flowing from the sixth pipeline into the generator cooling oil circuit;

[0027] A fourth throttle valve is provided on the third pipeline, and the fourth throttle valve is used to control the amount of oil flowing from the third pipeline into the clutch cooling oil circuit;

[0028] The fifth pipeline is provided with a fifth throttle valve, and the fifth throttle valve is used to control the amount of oil flowing from the fifth pipeline into the third pipeline.

[0029] Optionally, an overflow valve is provided on the second pipeline for returning part of the hydraulic oil on the second pipeline to the first oil pump.

[0030] Optionally, a cooler, a bypass valve, and a second filter are provided on the first pipeline, the inlet of the cooler is connected to the outlet of the first oil pump, the outlet of the cooler is connected to the inlet of the second filter and the inlet of the first throttle valve, the bypass valve is connected in parallel with the cooler, and the outlet of the second filter is connected to the first inlet and the second inlet of the first solenoid valve, the third pipeline, the second pipeline, and the fourth pipeline;

[0031] When the temperature of the hydraulic oil at the outlet of the first oil pump is lower than a preset temperature, the bypass valve opens; when the temperature of the hydraulic oil at the outlet of the first oil pump is higher than or equal to the preset temperature, the bypass valve closes.

[0032] Optionally, a one-way valve is further provided on the first pipeline, the one-way valve is connected in parallel with the second filter, and the flow direction of the one-way valve is the same as the flow direction of the second filter;

[0033] When the oil pressure resistance of the second filter is less than the opening pressure of the one-way valve, the one-way valve is closed; when the oil pressure resistance of the second filter is greater than or equal to the opening pressure of the one-way valve, the one-way valve is opened.

[0034] Optionally, a first filter is connected between the first oil tank and the first oil pump.

[0035] Optionally, a second solenoid valve is provided on the second oil circuit, and the inlet of the second oil pump is connected to the second oil tank;

[0036] The clutch is a hydraulic clutch. The second solenoid valve is connected between the outlet of the second oil pump and the oil cylinder of the clutch and is used to control the filling and draining of oil in the oil cylinder of the clutch to achieve pressure control of the clutch.

[0037] Optionally, the clutch includes a cylinder, an active end, and a passive end, wherein the piston rod of the cylinder is connected to the active end, and the passive end remains stationary; the interior of the cylinder body of the cylinder is divided into a control chamber and an airtight chamber by a piston, and an elastic return member is provided in the airtight chamber, wherein one end of the elastic return member abuts against the piston of the cylinder and the other end abuts against the inner wall of the cylinder body of the cylinder; the second solenoid valve is connected between the outlet of the second oil pump and the control chamber of the cylinder;

[0038] The second oil pump fills oil into the control chamber through the second solenoid valve, which can extend the piston rod so that the active end and the driven end are combined to achieve the engagement of the clutch; the oil pressure in the control chamber is controlled by the second solenoid valve, which can adjust the engagement force between the active end and the driven end to achieve the engagement force adjustment of the clutch; the oil discharge from the control chamber is controlled by the second solenoid valve, which can retract the piston rod and separate the active end and the driven end to achieve the disengagement of the clutch.

[0039] Optionally, the second solenoid valve is a three-position four-way valve, and the valve core of the second solenoid valve can slide and switch between a first position, a second position and a third position;

[0040] When the valve core of the second solenoid valve is in the first position, the hydraulic oil flowing out of the second oil pump flows into the oil cylinder of the clutch through the second solenoid valve to achieve oil filling of the clutch; after the clutch oil filling is completed, the clutch is engaged and the valve core of the second solenoid valve is switched to the second position;

[0041] When the valve core of the first solenoid valve is in the second position, the hydraulic oil flowing out of the second oil pump passes through the second solenoid valve, with a portion flowing into the oil cylinder of the clutch and the other portion flowing back to the second oil tank to adjust the pressure of the clutch;

[0042] When the clutch needs to be released, the valve core of the first solenoid valve is switched to the third position, and the hydraulic oil in the oil cylinder of the clutch flows back to the second oil tank through the second solenoid valve.

[0043] Optionally, the second solenoid valve has an oil inlet, an oil outlet, a first oil return port, and a second oil return port, wherein the oil inlet and the first oil return port are located on a side of the second solenoid valve close to the second oil pump, and the oil outlet and the second oil return port are located on a side of the second solenoid valve close to the clutch;

[0044] The oil inlet of the second solenoid valve is connected to the outlet of the second oil pump via a seventh pipeline, the first oil return port is connected to the second oil tank via an eighth pipeline, the oil outlet of the second solenoid valve is connected to the oil cylinder of the clutch via a ninth pipeline, and the second oil return port is connected to the second oil tank via a tenth pipeline;

[0045] When the valve core of the second solenoid valve is in the first position, the oil inlet is connected to the oil outlet, and the first oil return hole is connected to the second oil return hole;

[0046] When the valve core of the second solenoid valve is in the second position, the oil inlet is connected to the oil outlet and the second oil return port at the same time, and the first oil return hole is blocked;

[0047] When the valve core of the second solenoid valve is located at the third position, the oil inlet is communicated with the second oil return hole, and the oil outlet is communicated with the first oil return hole.

[0048] Optionally, a sixth throttle valve is provided on the tenth pipeline, and the sixth throttle valve is used to control the amount of oil flowing back from the second oil return port to the second oil tank.

[0049] Optionally, a third filter and a fourth filter are further provided on the tenth pipeline, the third filter is connected between the second oil return port and the sixth throttle valve, and the fourth filter is connected between the sixth throttle valve and the second oil tank.

[0050] Optionally, the ninth pipeline is connected to an exhaust valve for exhausting gas from the hydraulic oil in the ninth pipeline;

[0051] The pre-compression force of the exhaust valve is smaller than the KP value of the clutch.

[0052] Optionally, the ninth pipeline is connected to a pressure sensor for detecting the oil pressure in the ninth pipeline.

[0053] Optionally, a fifth filter is connected between the second oil tank and the inlet of the second oil pump;

[0054] The outlet side of the filter element of the fifth filter is provided with a uniform orifice plate to separate bubbles in the hydraulic oil.

[0055] On the other hand, an embodiment of the present invention further provides a hydraulic control system, comprising a clutch, a control unit, and the above-mentioned hydraulic device, wherein the control unit is electrically connected to the first throttle valve, the first oil pump, and the second oil pump respectively;

[0056] The control unit is capable of controlling the opening degree of the first throttle valve, the rotation speed of the first oil pump, and the rotation speed of the second oil pump.

[0057] On the other hand, an embodiment of the present invention further provides a vehicle including the above-mentioned hydraulic control system.

[0058] On the other hand, an embodiment of the present invention further provides a control method based on the above-mentioned hydraulic device, comprising:

[0059] The hydraulic oil in the first oil tank is sucked by the first oil pump and supplied to the first oil circuit to cool and lubricate the electromechanical coupling transmission;

[0060] The hydraulic oil in the second oil tank is sucked by the second oil pump and supplied to the second oil circuit to control the engagement and disengagement of the clutch of the electromechanical coupling transmission;

[0061] The opening of the first throttle valve is adjusted to control the amount of oil supplied from the first oil circuit to the second oil tank.

[0062] Optionally, it also includes:

[0063] Control the on / off of oil supply from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve; wherein the first solenoid valve is connected between the outlet of the first oil pump and the generator cooling oil circuit and the clutch cooling oil circuit.

[0064] Optionally, the first solenoid valve is a three-position four-way valve, and controlling the on-off of the oil supply from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve includes:

[0065] When the vehicle is in a mode switching state, the valve core of the first solenoid valve is controlled to be in the first position, so that the hydraulic oil in the first oil circuit flows into the clutch cooling oil circuit and the generator cooling oil circuit respectively through the first solenoid valve;

[0066] When the vehicle is in the extended-range mode or the hybrid mode, the valve core of the first solenoid valve is controlled to be in the second position, so that the hydraulic oil in the first oil circuit flows into the generator cooling oil circuit only through the first solenoid valve;

[0067] When the vehicle is in the pure electric mode, the valve core of the first solenoid valve is controlled to be in the third position, so that the hydraulic oil in the first oil circuit is cut off at the first solenoid valve.

[0068] Optionally, it also includes:

[0069] The filling and draining of the clutch cylinder are controlled by the second solenoid valve to achieve clutch pressure control.

[0070] Optionally, the second solenoid valve is a three-position four-way valve, and controlling the filling and draining of the clutch cylinder by the second solenoid valve includes:

[0071] Controlling the valve core of the second solenoid valve to be in the first position, so that the hydraulic oil flowing out of the second oil pump flows into the oil cylinder of the clutch through the second solenoid valve to achieve oil filling of the clutch;

[0072] After the clutch is filled with oil, the clutch is engaged, and the valve core of the second solenoid valve is switched to the second position, so that the hydraulic oil flowing out of the second oil pump passes through the second solenoid valve, part of which flows into the clutch cylinder and the other part flows back to the second oil tank to adjust the pressure of the clutch;

[0073] Switch the valve core of the first solenoid valve to the third position, so that the hydraulic oil in the clutch cylinder flows back to the second oil tank through the second solenoid valve, thereby achieving oil release and separation of the clutch. BRIEF DESCRIPTION OF THE DRAWINGS

[0074] FIG1 is a schematic diagram of a hydraulic device provided by one embodiment of the present invention;

[0075] 2 is a schematic diagram of a valve core of a first solenoid valve of a hydraulic device provided by an embodiment of the present invention being in a first position;

[0076] 3 is a schematic diagram of a valve core of a first solenoid valve of a hydraulic device provided by an embodiment of the present invention being in a second position;

[0077] 4 is a schematic diagram of a hydraulic device according to an embodiment of the present invention, in which the valve core of the first solenoid valve is in a third position;

[0078] 5 is a schematic diagram of a valve core of a second solenoid valve of a hydraulic device provided by an embodiment of the present invention being in a first position;

[0079] 6 is a schematic diagram of a second solenoid valve of a hydraulic device provided by an embodiment of the present invention, in which the valve core is in a second position;

[0080] 7 is a schematic diagram of a second solenoid valve of a hydraulic device provided by an embodiment of the present invention, in which the valve core is in a third position;

[0081] FIG8 is a block diagram of a control method provided by an embodiment of the present invention.

[0082] The following are the descriptions of the reference numerals:

[0083] 10. Hydraulic device; 20. Clutch; 201. Cylinder; 2011. Piston rod; 2012. Cylinder body; 2013. Control chamber; 2014. Airtight chamber; 2015. Elastic return member; 2016. Piston; 202. Active end; 203. Driven end; 30. Drive motor cooling oil circuit; 40. Clutch cooling oil circuit; 50. Generator cooling oil circuit;

[0084] 1. Cooling and lubricating oil circuit; 11. First oil tank; 12. First oil pump; 13. First oil circuit; 131. First solenoid valve; 132. First pipeline; 1321. Cooler; 1322. Bypass valve; 1323. Check valve; 133. Second pipeline; 1331. Overflow valve; 134. Third pipeline; 135. Fourth pipeline; 136. Fifth pipeline; 137. Sixth pipeline;

[0085] 2. Pressure control oil circuit; 21. Second oil tank; 22. Second oil pump; 23. Second oil circuit; 231. Second solenoid valve; 232. First pipeline; 233. Eighth pipeline; 234. Ninth pipeline; 2341. Exhaust valve; 2342. Pressure sensor; 235. Tenth pipeline;

[0086] 3. Oil return pipe; 4. Overflow pipe;

[0087] R1, first throttle valve; R2, second throttle valve; R3, third throttle valve; R4, fourth throttle valve; R5, fifth throttle valve; R6, sixth throttle valve; F1, first filter; F2, second filter; F3, third filter; F4, fourth filter; F5, fifth filter. DETAILED DESCRIPTION

[0088] In order to make the technical problems, technical solutions and beneficial effects solved by the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0089] 1 , a hydraulic control system provided by an embodiment of the present invention includes a hydraulic device 10 , a clutch 20 , and a control unit.

[0090] The control unit may be a separate component, or the control unit may be a transmission control unit.

[0091] The hydraulic device 10 includes a cooling and lubricating oil circuit 1 and a pressure control oil circuit 2; the cooling and lubricating oil circuit 1 includes a first oil tank 11, a first oil pump 12 and a first oil circuit 13, the first oil pump 12 is connected between the first oil tank 11 and the first oil circuit 13, the first oil tank 11 is used to supply oil to the first oil pump 12, and the first oil pump 12 is used to provide hydraulic oil to the first oil circuit 13 to cool and lubricate the electromechanical coupling transmission through the first oil circuit 13.

[0092] The pressure control oil circuit 2 includes a second oil tank 21, a second oil pump 22 and a second oil circuit 23. The second oil pump 22 is connected between the second oil tank 21 and the second oil circuit 23. The second oil tank 21 is used to supply oil to the second oil pump 22. The second oil pump 22 is used to provide hydraulic oil to the second oil circuit 23 to control the engagement and disengagement of the clutch 20 of the electromechanical coupling transmission through the second oil circuit 23.

[0093] The second oil circuit 23 is provided with a first throttle valve R1, which is connected between the first oil circuit 13 and the second oil tank 21 and is used to control the amount of oil supplied from the first oil circuit 13 to the second oil tank 21. The control unit is electrically connected to the first throttle valve R1, the first oil pump 12, and the second oil pump 22. Specifically, the control terminals of the first throttle valve R1, the first oil pump 12, and the second oil pump 22 are connected to the control unit via signal lines. The control unit is capable of controlling the opening of the first throttle valve R1, the rotational speed of the first oil pump 12, and the rotational speed of the second oil pump 22. Specifically, the control unit can request corresponding rotational speeds from the first oil pump 12 and the second oil pump 22 based on speed requirements.

[0094] The first oil pump 12 and the second oil pump 22 are preferably electronic oil pumps for ease of control.

[0095] According to the hydraulic device and hydraulic control system of the embodiment of the present invention, a first throttle valve R1 is disposed between the first oil circuit 13 of the cooling and lubricating oil circuit 1 (low-pressure oil circuit) and the second oil tank 21 of the pressure control oil circuit 2 (high-pressure oil circuit). The first throttle valve R1 is used to control the amount of oil supplied from the first oil circuit 13 to the second oil tank 21. This allows excess hydraulic oil in the cooling and lubricating oil circuit 1 to flow not directly back to the first oil tank of the cooling and lubricating oil circuit 1 but instead to be supplied to the second oil tank 21 for use in the pressure control oil circuit 2 to control the pressure of the clutch 20, thus achieving efficient utilization of the hydraulic oil.

[0096] In one embodiment, referring to FIG1 , the first throttle valve R1 is disposed on an oil return pipe 3 , one end of which is connected to the first oil passage 13 , and the other end of which is connected to the second oil tank 21 . The connection point between one end of the oil return pipe 3 and the first oil passage 13 is located on the outlet side of the first oil pump 12 .

[0097] In one embodiment, the first oil tank 11 is provided independently of the second oil tank 21. This separates the pressure control circuit 2 from the transmission's oil stirring (which occurs in the first oil tank 11), reduces the amount of gas in the hydraulic oil in the pressure control circuit 2, and mitigates the impact of bubble collapse on the hydraulic oil's pressure stability. In one embodiment, referring to Figure 1 , the first oil tank 11 and the second oil tank 21 are connected via an overflow pipe 4, allowing any hydraulic oil overflowing from the second oil tank 21 to flow back into the first oil tank 11.

[0098] The first and second oil tanks 11 and 21 are located within the electromechanical coupling transmission assembly. The first oil tank 11 serves as the main oil tank, supplying oil to the low-pressure oil circuit (cooling and lubrication oil circuit) while also providing partial splash lubrication through gear agitation. The second oil tank 21 supplies oil only to the high-pressure oil circuit (pressure control oil circuit 2). The oil supply to the second oil tank 21 is determined by the outlet flow rate of the first throttle valve R1 and the return oil from the overflow pipe 4, and is completely independent of the overall oil agitation system.

[0099] In one embodiment, referring to FIG1 , a first solenoid valve 131 is provided in the first oil circuit 13. The inlet of the first oil pump 12 is connected to the first oil tank 11. The cooling oil circuit of the electromechanical transmission includes a drive motor cooling oil circuit 30, a clutch cooling oil circuit 40, and a generator cooling oil circuit 50. The second oil circuit 13 connects to the clutch cooling oil circuit 40 and the drive motor cooling oil circuit 30 to enable oil supply to the clutch cooling oil circuit 40 and the drive motor cooling oil circuit 30 without passing through the first solenoid valve 131. The first solenoid valve 131 is connected between the outlet of the first oil pump 12 and the generator cooling oil circuit 50 and the clutch cooling oil circuit 40 to control the on / off flow of oil from the first oil circuit 13 to the generator cooling oil circuit 50 and the clutch cooling oil circuit 40 via the first solenoid valve 131.

[0100] In one embodiment, referring to Figures 1 to 4 , the first solenoid valve 131 is a three-position, four-way valve, preferably a three-position, four-way mechanical spool valve, driven by an electromagnet. The valve core of the first solenoid valve 131 is slidably disposed within a housing of the first solenoid valve 131. The first solenoid valve 131 is electrically connected to a control unit, which controls the sliding movement of the valve core of the first solenoid valve 131 between the first, second, and third positions.

[0101] When the valve core of the first solenoid valve 131 is in the first position, the hydraulic oil in the first oil circuit 13 flows into the clutch cooling oil circuit 40 and the generator cooling oil circuit 50 respectively through the first solenoid valve 131; when the valve core of the first solenoid valve 131 is in the second position, the hydraulic oil in the first oil circuit 13 flows into the generator cooling oil circuit 50 only through the first solenoid valve 131 (i.e., the oil circuit from the first solenoid valve 131 to the clutch cooling oil circuit 40 is disconnected). When the valve core of the first solenoid valve 131 is in the third position, the hydraulic oil in the first oil circuit 13 is cut off at the first solenoid valve 131, i.e., the oil circuits from the first solenoid valve 131 to the clutch cooling oil circuit 40 and the generator cooling oil circuit 50 are both disconnected).

[0102] When the vehicle is in a mode-switching state, the valve core of first solenoid valve 131 is controlled to the first position (see Figure 2). The oil supply from first oil circuit 13 to both generator cooling oil circuit 50 and clutch cooling oil circuit 40 via first solenoid valve 131 is unblocked, allowing a portion of the hydraulic oil in first oil circuit 13 to flow through first solenoid valve 131 into clutch cooling oil circuit 40 and generator cooling oil circuit 50, respectively. Furthermore, another portion of the hydraulic oil in first oil circuit 13 bypasses first solenoid valve 131 and flows directly into clutch cooling oil circuit 40 and drive motor cooling oil circuit 30. This allows high-flow cooling of the clutch 20 in sliding mode while also meeting the cooling requirements of the generator and drive motor.

[0103] When the vehicle is in extended-range or hybrid mode, the valve core of first solenoid valve 131 is controlled to the second position (see Figure 3). Oil supply from first oil circuit 13 to generator cooling oil circuit 50 via first solenoid valve 131 is opened, while oil supply from first oil circuit 13 to clutch cooling oil circuit 40 via first solenoid valve 131 is cut off. This allows a portion of the hydraulic oil in first oil circuit 13 to flow solely through first solenoid valve 131 into generator cooling oil circuit 50. Furthermore, another portion of the hydraulic oil in first oil circuit 13 flows directly into clutch cooling oil circuit 40 and drive motor cooling oil circuit 30, bypassing first solenoid valve 131. This allows low-flow cooling of clutch 20 while meeting the cooling requirements of the generator and drive motor.

[0104] When the vehicle is in pure electric mode, the valve core of first solenoid valve 131 is controlled to the third position (see Figure 4), shutting off the hydraulic oil in first oil circuit 13 at the first solenoid valve. This shuts off the oil supply from first oil circuit 13 to both the generator cooling oil circuit 50 and the clutch cooling oil circuit 40 via first solenoid valve 131. The hydraulic oil in first oil circuit 13 flows directly into the clutch cooling oil circuit 40 and the drive motor cooling oil circuit 30, bypassing first solenoid valve 131. This allows for low-flow cooling of the clutch 20 and the drive motor, while the generator cooling oil circuit is shut off.

[0105] In one embodiment, referring to Figures 1 to 4, the first inlet and the second inlet of the first solenoid valve 131 are connected to the outlet of the first oil pump 12 through a first pipeline 132, the first inlet and the second inlet of the first solenoid valve 131 are connected to the first oil tank 11 and the inlet of the first oil pump 12 through a second pipeline 133, the first pipeline 132 is connected to the clutch cooling oil circuit 40 through a third pipeline 134, the connection point between the first pipeline 132 and the third pipeline 134 is located between the outlet of the first oil pump 12 and the first inlet of the first solenoid valve 131, and the second pipeline 133 is connected to the drive motor cooling oil circuit 30 through a fourth pipeline 135.

[0106] The first outlet of the first solenoid valve 131 is connected to the third pipeline 134 through a fifth pipeline 136 , and the second outlet of the first solenoid valve 131 is connected to the generator cooling oil circuit 50 through a sixth pipeline 137 .

[0107] Referring to Figure 2, when the valve core of the first solenoid valve is in the first position, the first inlet is connected to the first outlet, and the second inlet is connected to the second outlet; the oil supply from the first oil circuit 13 to the generator cooling oil circuit 50 and the clutch cooling oil circuit 40 is conducted through the first solenoid valve 131.

[0108] Referring to Figure 3, when the valve core of the first solenoid valve is in the second position, the first inlet and the first outlet are blocked, and the second inlet and the second outlet are connected; the oil supply from the first oil circuit 13 to the generator cooling oil circuit 50 through the first solenoid valve 131 is conducted, and the oil supply from the first oil circuit 13 to the clutch cooling oil circuit 40 through the first solenoid valve 131 is disconnected.

[0109] As shown in Figure 4 , when the valve core of the first solenoid valve is in the third position, the first inlet is blocked from the first outlet, and the second inlet is blocked from the second outlet. This shuts off the hydraulic oil flow in the first oil circuit 13 at the first solenoid valve. This also cuts off the oil supply from the first oil circuit 13 to both the generator cooling oil circuit 50 and the clutch cooling oil circuit 40 via the first solenoid valve 131.

[0110] In one embodiment, referring to FIG1 , a second throttle valve R2 is provided on the fourth pipeline 135 . The second throttle valve R2 is used to control the amount of oil flowing from the fourth pipeline 135 into the drive motor cooling oil circuit 30 . The second throttle valve R2 is electrically connected to a control unit, which controls the opening of the second throttle valve R2 .

[0111] In one embodiment, referring to FIG1 , a third throttle valve R3 is provided on the sixth pipeline 137. The third throttle valve R3 is used to control the amount of oil flowing from the sixth pipeline 137 into the generator cooling oil circuit 50. The third throttle valve R3 is electrically connected to a control unit, which controls the opening of the third throttle valve R3.

[0112] In one embodiment, referring to FIG1 , a fourth throttle valve R4 is provided on the third pipeline 134 , and the fourth throttle valve R4 is used to control the amount of oil flowing from the third pipeline 134 into the clutch cooling oil circuit 40 ; the fourth throttle valve R4 is electrically connected to a control unit, and the control unit controls the opening of the fourth throttle valve R4 .

[0113] In one embodiment, referring to FIG1 , a fifth throttle valve R5 is provided on the fifth pipeline 136 to control the amount of oil flowing from the fifth pipeline 136 into the third pipeline 134. The hydraulic oil in the fifth pipeline 136 and the third pipeline 134 merge and then flow into the clutch cooling oil circuit 40.

[0114] In one embodiment, referring to FIG. 1 , a relief valve 1331 is provided on the second pipeline 133 for returning part of the hydraulic oil (excess hydraulic oil) on the second pipeline 133 to the first oil pump 12 .

[0115] In one embodiment, referring to FIG. 1 , a first filter F1 is connected between the first oil tank 11 and the first oil pump 12 , for filtering the hydraulic oil coming out of the first oil tank 11 .

[0116] In one embodiment, referring to Figure 1 , the first pipeline 132 is provided with a cooler 1321, a bypass valve 1322, and a second filter F2. The inlet of the cooler 1321 is connected to the outlet of the first oil pump 12, while the outlet of the cooler 1321 is connected to the inlet of the second filter F2 and the inlet of the first throttle valve R1. The connection point between one end of the oil return pipe 3 and the first oil pipeline 13 is located between the outlet of the first oil pump 12 and the inlet of the cooler 1321. The bypass valve 1322 is connected in parallel with the cooler 1321. The outlet of the second filter F2 is connected to the first and second inlets of the first solenoid valve 131, the third pipeline 134, the second pipeline 133, and the fourth pipeline 135. When the hydraulic oil temperature at the outlet of the first oil pump 12 is lower than a preset temperature, the resistance of cooler 1321 is high, and a very small portion of the hydraulic oil flows through cooler 1321 to the second filter F2. At this time, the bypass valve 1322 opens, and the branch path of bypass valve 1322 bypasses cooler 1321 to flow to the second filter F2. The majority of the hydraulic oil flows through the branch path of bypass valve 1322 to bypass cooler 1321 and flow to the second filter F2. When the hydraulic oil temperature at the outlet of the first oil pump 12 is greater than or equal to a preset temperature, the bypass valve 1322 closes, the resistance of cooler 1321 is low, and the hydraulic oil flows through cooler 1321 to the second filter F2. The second filter F2 can filter impurities in the hydraulic oil flowing out of the cooler 1321.

[0117] In one embodiment, the bypass valve 1322 can be a pressure differential bypass valve, such as a paraffin bypass valve. When the temperature of the hydraulic oil at the outlet of the first oil pump 12 is lower than a preset temperature (e.g., 65 degrees Celsius), the paraffin is not melted, and the bypass valve 1322 opens. When the temperature of the hydraulic oil at the outlet of the first oil pump 12 is higher than or equal to the preset temperature, the paraffin is melted, and the bypass valve 1322 gradually closes.

[0118] Of course, in another embodiment, a combination of a solenoid valve and a temperature sensor can be used to replace the bypass valve 1322. The temperature sensor detects the temperature of the hydraulic oil at the outlet of the first oil pump 12 and transmits it to the control unit. The control unit controls the opening and closing of the solenoid valve based on the temperature signal, thus achieving a function similar to that of the bypass valve 1322.

[0119] The bypass valve 1322 can solve the problem of normal oil supply to the cooling and lubricating oil circuit 1 at low temperatures, so that the electromechanical coupling transmission can still be cooled and lubricated in a low temperature environment.

[0120] In one embodiment, referring to FIG1 , a one-way valve 1323 is further provided on the first pipeline 132. The one-way valve 1323 is connected in parallel with the second filter F2, and the flow direction of the one-way valve 1323 is the same as that of the second filter F2. When the oil pressure resistance of the second filter F2 is less than the opening pressure of the one-way valve (the filter element of the second filter F2 is relatively clean), the one-way valve 1323 closes (the steel ball is pushed by the spring to close the internal flow path of the one-way valve), and the hydraulic oil flows through the second filter F2 to the cooling oil circuit of the electromechanical transmission. When the oil pressure resistance of the second filter F2 is greater than or equal to the opening pressure of the one-way valve 1323 (the filter element of the second filter F2 is clogged with particles), the one-way valve F2 opens (the hydraulic oil pushes the steel ball away, clearing the internal flow path of the one-way valve).

[0121] The one-way valve 1323 can ensure normal oil supply when the filter element of the second filter F2 is blocked by particles, so that the electromechanical coupling transmission can still be cooled and lubricated when the filter element of the second filter F2 is blocked by particles.

[0122] Of course, in another embodiment, a combination of a solenoid valve and a pressure sensor can be used to replace the one-way valve 1323. The pressure sensor detects the oil pressure of the second filter F2 and transmits it to the control unit. The control unit controls the opening and closing of the solenoid valve based on the oil pressure signal, thus achieving a function similar to that of the one-way valve 1323.

[0123] In one embodiment, referring to FIG1 , a second solenoid valve 231 is provided on the second oil circuit 23, and the inlet of the second oil pump 22 is connected to the second oil tank 21. The clutch 20 is a hydraulic clutch, and the second solenoid valve 231 is connected between the outlet of the second oil pump 22 and the oil cylinder 201 of the clutch 20 to control the filling and draining of oil in the oil cylinder 201 of the clutch 20, thereby achieving pressure control of the clutch 20.

[0124] In one embodiment, referring to FIG1 , the clutch includes a cylinder 201, an active end 202, and a passive end 203. The piston rod 2011 of the cylinder 201 is connected to the active end 202, and the passive end 203 remains stationary. The interior of the cylinder body 2012 of the cylinder 201 is divided into a control chamber 2013 and an airtight chamber 2014 by a piston. An elastic return member 2015 (such as a spring) is provided in the airtight chamber 2014. One end of the elastic return member 2015 abuts against the piston 2016 of the cylinder 201, and the other end abuts against the inner wall of the cylinder body 2012 of the cylinder 201. The second solenoid valve 231 is connected to the outlet of the second oil pump 22 and the control chamber 2013 of the cylinder 201. 013; the second oil pump 22 fills oil into the control chamber 2013 through the second solenoid valve 231, which can make the piston rod 2011 extend, so that the active end 202 and the driven end 203 are combined, and the clutch 20 is combined; the oil pressure of the control chamber 2013 is controlled by the second solenoid valve 231, which can adjust the combination force of the active end 202 and the driven end 203, and realize the combination force adjustment of the clutch 202 (pressure adjustment of the clutch 20); the control chamber 2013 is controlled to discharge oil by the second solenoid valve 231, which can retract the piston rod 2011, separate the active end 202 and the driven end 203, and realize the separation of the clutch 20.

[0125] In one embodiment, referring to FIG1 , the second solenoid valve 231 is a three-position, four-way valve, preferably a three-position, four-way direct-drive solenoid valve, i.e., it is driven by a motor. The valve core of the second solenoid valve 231 can slide and switch between a first position, a second position, and a third position. The second solenoid valve 231 is electrically connected to a control unit, which controls the valve core of the second solenoid valve 131 to slide and switch between the first position, the second position, and the third position.

[0126] When the valve core of the second solenoid valve 231 is in the first position (see Figure 5), the hydraulic oil flowing out of the second oil pump 22 flows into the control chamber 2013 of the oil cylinder 201 of the clutch 20 through the second solenoid valve 231 to realize the oil filling of the clutch 20; after the oil filling of the clutch 20 is completed, the clutch 20 is engaged, and the control unit controls the valve core of the second solenoid valve 231 to switch to the second position.

[0127] When the valve core of the first solenoid valve is in the second position (see Figure 6), the hydraulic oil flowing out of the second oil pump 22 passes through the second solenoid valve 231, and a portion flows into the control chamber 2013 of the oil cylinder 201 of the clutch 20, and the other portion flows back to the second oil tank 21 to adjust the pressure of the clutch 20.

[0128] When the clutch 20 needs to be released, the valve core of the first solenoid valve 231 switches to the third position (see FIG. 7 ), and the hydraulic oil in the oil cylinder 201 of the clutch 20 flows back to the second oil tank 21 through the second solenoid valve 231 .

[0129] In one embodiment, referring to Figures 5-7, the second solenoid valve 231 has an oil inlet, an oil outlet, a first oil return port and a second oil return port, the oil inlet and the first oil return port are located on the side of the second solenoid valve 231 close to the second oil pump 22, and the oil outlet and the second oil return port are located on the side of the second solenoid valve 231 close to the clutch 20.

[0130] The oil inlet of the second solenoid valve 231 is connected to the outlet of the second oil pump 22 through the seventh pipeline 232, the first oil return port is connected to the second oil tank 21 through the eighth pipeline 233, the oil outlet of the second solenoid valve 232 is connected to the control chamber 2013 of the oil cylinder 201 of the clutch 20 through the ninth pipeline 234, and the second oil return port is connected to the second oil tank 21 through the tenth pipeline 235.

[0131] When the valve core of the second solenoid valve 231 is in the first position (see Figure 5), the oil inlet is connected to the oil outlet, and the first oil return hole is connected to the second oil return hole; the hydraulic oil flowing out of the second oil pump 22 flows into the control chamber 2013 of the oil cylinder 201 of the clutch 20 through the second solenoid valve 231 to achieve rapid oil filling of the clutch 20.

[0132] When the valve core of the second solenoid valve 231 is in the second position (see Figure 6), the oil inlet is connected to the oil outlet and the second oil return port at the same time, and the first oil return hole is blocked; after the hydraulic oil flowing out of the second oil pump 22 passes through the second solenoid valve 231, a part of it flows into the control chamber 2013 of the oil cylinder 201 of the clutch 20, and the other part flows back to the second oil tank 21 to adjust the pressure of the clutch 20, thereby realizing pressure control after the clutch 20 is engaged. The pressure of the clutch 20 can be continuously adjusted by changing the speed of the second oil pump 22.

[0133] When the valve core of the second solenoid valve 231 is in the third position (see FIG. 7 ), the oil inlet communicates with the second oil return hole, and the oil outlet communicates with the first oil return hole. The hydraulic oil in the oil cylinder 201 of the clutch 20 flows back to the second oil tank 21 through the second solenoid valve 231 , and the oil in the oil cylinder 201 of the clutch 20 is drained, enabling rapid disengagement of the clutch 20.

[0134] By controlling the different positions of the second solenoid valve 231, the problem of slow clutch engagement and disengagement speeds in the hydraulic control system in the prior art can be effectively solved, further improving the response speed of vehicle mode switching.

[0135] In one embodiment, referring to FIG1 , a sixth throttle valve R6 is provided on the tenth pipeline 235. The sixth throttle valve R6 is used to control the amount of oil returning from the second oil return port to the second oil tank 21. The sixth throttle valve R6 is electrically connected to a control unit, which controls the opening of the sixth throttle valve R6.

[0136] During the oil filling stage of the clutch 20, the second solenoid valve 231 cuts off the passage between the sixth throttle valve R6 and the outlet of the second oil pump 22 to achieve rapid oil filling; during the separation stage of the clutch 20, a fixed valve hole (second oil return port) is used to quickly drain the oil instead of the sixth throttle valve R6, thereby increasing the separation speed of the clutch 20.

[0137] In one embodiment, referring to FIG1 , a third filter F3 and a fourth filter F4 are further provided on the tenth pipeline 235. The third filter F3 is connected between the second oil return port and the sixth throttle valve R6, and the fourth filter F4 is connected between the sixth throttle valve R6 and the second fuel tank 21. The third filter F3 can filter the hydraulic oil before entering the sixth throttle valve R6, and the fourth filter F4 can filter the hydraulic oil after exiting the sixth throttle valve R6, thereby ensuring the cleanliness of the hydraulic oil in the second fuel tank 21.

[0138] In one embodiment, referring to FIG. 1 , the ninth pipeline 234 is connected to an exhaust valve 2341 for exhausting gas from the hydraulic oil in the ninth pipeline 234 to reduce the impact of bubble bursting on the pressure stability of the hydraulic oil.

[0139] The pre-compression force of the exhaust valve 2341 is smaller than the KP (kiss point) value of the clutch 20. The KP value refers to the engagement force value when the clutch 20 is at the half-engagement point.

[0140] In one embodiment, referring to FIG. 1 , the ninth pipeline 234 is connected to a pressure sensor 2342 for detecting the oil pressure in the ninth pipeline 234 .

[0141] In one embodiment, referring to FIG. 1 , a fifth filter F5 is connected between the second oil tank 21 and the inlet of the second oil pump 22 .

[0142] Preferably, a uniform orifice plate is provided on the outlet side of the filter element of the fifth filter F5 to separate bubbles in the hydraulic oil and reduce the impact of bubble burst on the pressure stability of the hydraulic oil.

[0143] The hydraulic device and hydraulic control system of the present invention, by identifying the vehicle's operating mode, adjusts the rotational speeds of the first oil pump 12 and the second oil pump 22 to meet the flow and pressure requirements of the cooling lubricating oil circuit 1 (low-pressure oil circuit) and the pressure control oil circuit 2 (high-pressure oil circuit), respectively, thereby achieving flow and pressure control. Furthermore, the cooling lubricating oil circuit 1 (low-pressure oil circuit) and the pressure control oil circuit 2 (high-pressure oil circuit) are independent of each other, allowing the pressure and flow of the cooling lubricating oil circuit 1 (low-pressure oil circuit) and the pressure control oil circuit 2 (high-pressure oil circuit) to be supplied on demand, thereby reducing the energy consumption of the first oil pump 12 and the second oil pump 22.

[0144] In addition, an embodiment of the present invention further provides a vehicle including the above-mentioned hydraulic control system.

[0145] In addition, referring to FIG8 , an embodiment of the present invention further provides a control method based on the above-mentioned hydraulic device, including:

[0146] The hydraulic oil in the first oil tank is sucked by the first oil pump and supplied to the first oil circuit to cool and lubricate the electromechanical coupling transmission.

[0147] The hydraulic oil in the second oil tank is sucked by the second oil pump and supplied to the second oil circuit to control the engagement and release of the clutch of the electromechanical coupling transmission.

[0148] The opening of the first throttle valve is adjusted to control the amount of oil supplied from the first oil circuit to the second oil tank.

[0149] In one embodiment, it further includes:

[0150] Control the on / off of oil supply from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve; wherein the first solenoid valve is connected between the outlet of the first oil pump and the generator cooling oil circuit and the clutch cooling oil circuit.

[0151] In one embodiment, the first solenoid valve is a three-position four-way valve, and controlling the on-off of the oil supply from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve includes:

[0152] When the vehicle is in a mode switching state, the valve core of the first solenoid valve is controlled to be in the first position, so that the hydraulic oil in the first oil circuit flows into the clutch cooling oil circuit and the generator cooling oil circuit respectively through the first solenoid valve.

[0153] When the vehicle is in the extended-range mode or the hybrid mode, the valve core of the first solenoid valve is controlled to be in the second position, so that the hydraulic oil in the first oil circuit flows into the generator cooling oil circuit only through the first solenoid valve.

[0154] When the vehicle is in the pure electric mode, the valve core of the first solenoid valve is controlled to be in the third position, so that the hydraulic oil in the first oil circuit is cut off at the first solenoid valve.

[0155] In one embodiment, it further includes:

[0156] The filling and draining of the clutch cylinder are controlled by the second solenoid valve to achieve clutch pressure control.

[0157] In one embodiment, the second solenoid valve is a three-position four-way valve, and controlling the filling and draining of the clutch cylinder by the second solenoid valve includes:

[0158] The valve core of the second solenoid valve is controlled to be in the first position, so that the hydraulic oil flowing out of the second oil pump flows into the oil cylinder of the clutch through the second solenoid valve to realize oil filling of the clutch.

[0159] After the clutch is filled with oil, the clutch is engaged and the valve core of the second solenoid valve is switched to the second position, so that the hydraulic oil flowing out of the second oil pump passes through the second solenoid valve, and part of it flows into the clutch cylinder, and the other part flows back to the second oil tank to adjust the pressure of the clutch.

[0160] Switch the valve core of the first solenoid valve to the third position, so that the hydraulic oil in the clutch cylinder flows back to the second oil tank through the second solenoid valve, thereby achieving oil release and separation of the clutch.

[0161] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A hydraulic device, characterized in that: Including cooling lubrication oil circuit and pressure control oil circuit; The cooling and lubricating oil circuit includes a first oil tank, a first oil pump, and a first oil circuit. The first oil pump is connected between the first oil tank and the first oil circuit. The first oil tank is used to supply oil to the first oil pump. The first oil pump is used to provide hydraulic oil to the first oil circuit to cool and lubricate the electromechanical coupling transmission through the first oil circuit. The pressure control oil circuit includes a second oil tank, a second oil pump, and a second oil circuit. The second oil pump is connected between the second oil tank and the second oil circuit. The second oil tank is used to supply oil to the second oil pump. The second oil pump is used to provide hydraulic oil to the second oil circuit to control the engagement and disengagement of the clutch of the electromechanical coupling transmission through the second oil circuit. The second oil circuit is provided with a first throttle valve, which is connected between the first oil circuit and the second oil tank and is used to control the amount of oil supplied from the first oil circuit to the second oil tank.

2. The hydraulic device according to claim 1, characterized in that The first oil tank is provided independently of the second oil tank.

3. The hydraulic device according to claim 2, characterized in that: The first oil tank is connected to the second oil tank through an overflow pipe, so that the hydraulic oil overflowing from the second oil tank can flow back to the first oil tank.

4. The hydraulic device according to claim 1, characterized in that The first oil circuit is provided with a first solenoid valve, and the inlet of the first oil pump is connected to the first oil tank; the cooling oil circuit of the electromechanical coupling transmission includes a drive motor cooling oil circuit, a clutch cooling oil circuit, and a generator cooling oil circuit, and the second oil circuit is connected to the clutch cooling oil circuit and the drive motor cooling oil circuit; The first solenoid valve is connected between the outlet of the first oil pump and the generator cooling oil circuit and the clutch cooling oil circuit, and is used to control the on / off supply of oil from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve.

5. The hydraulic device according to claim 4, characterized in that: The first solenoid valve is a three-position four-way valve, and the valve core of the first solenoid valve can slide and switch between a first position, a second position and a third position; When the valve core of the first solenoid valve is in the first position, the hydraulic oil in the first oil circuit flows into the clutch cooling oil circuit and the generator cooling oil circuit respectively through the first solenoid valve; When the valve core of the first solenoid valve is in the second position, the hydraulic oil in the first oil circuit flows into the generator cooling oil circuit only through the first solenoid valve; When the valve core of the first solenoid valve is in the third position, the hydraulic oil in the first oil circuit is cut off at the first solenoid valve.

6. The hydraulic device according to claim 5, characterized in that: The first inlet and the second inlet of the first solenoid valve are connected to the outlet of the first oil pump through a first pipeline, the first inlet and the second inlet of the first solenoid valve are connected to the first oil tank and the inlet of the first oil pump through a second pipeline, the first pipeline is connected to the clutch cooling oil circuit through a third pipeline, and the connection point between the first pipeline and the third pipeline is located between the outlet of the first oil pump and the first inlet of the first solenoid valve, and the second pipeline is connected to the drive motor cooling oil circuit through a fourth pipeline; The first outlet of the first solenoid valve is connected to the third pipeline through a fifth pipeline, and the second outlet of the first solenoid valve is connected to the generator cooling oil circuit through a sixth pipeline; When the valve core of the first solenoid valve is in the first position, the first inlet is connected to the first outlet, and the second inlet is connected to the second outlet; When the valve core of the first solenoid valve is in the second position, the first inlet is blocked from the first outlet, and the second inlet is connected to the second outlet; When the valve core of the first solenoid valve is located at the third position, the first inlet is blocked from the first outlet, and the second inlet is blocked from the second outlet.

7. The hydraulic device according to claim 6, characterized in that The fourth pipeline is provided with a second throttle valve, and the second throttle valve is used to control the amount of oil flowing from the fourth pipeline into the drive motor cooling oil circuit; The sixth pipeline is provided with a third throttle valve, and the third throttle valve is used to control the amount of oil flowing from the sixth pipeline into the generator cooling oil circuit; A fourth throttle valve is provided on the third pipeline, and the fourth throttle valve is used to control the amount of oil flowing from the third pipeline into the clutch cooling oil circuit; The fifth pipeline is provided with a fifth throttle valve, and the fifth throttle valve is used to control the amount of oil flowing from the fifth pipeline into the third pipeline.

8. The hydraulic device according to claim 6, characterized in that: The second pipeline is provided with an overflow valve for returning part of the hydraulic oil in the second pipeline to the first oil pump.

9. The hydraulic device according to claim 6, characterized in that: The first pipeline is provided with a cooler, a bypass valve and a second filter, the inlet of the cooler is connected to the outlet of the first oil pump, the outlet of the cooler is connected to the inlet of the second filter and the inlet of the first throttle valve, the bypass valve is connected in parallel with the cooler, and the outlet of the second filter is connected to the first inlet and the second inlet of the first solenoid valve, the third pipeline, the second pipeline and the fourth pipeline; When the temperature of the hydraulic oil at the outlet of the first oil pump is lower than a preset temperature, the bypass valve opens; when the temperature of the hydraulic oil at the outlet of the first oil pump is higher than or equal to the preset temperature, the bypass valve closes.

10. The hydraulic device according to claim 9, characterized in that: A one-way valve is further provided on the first pipeline, the one-way valve is connected in parallel with the second filter, and the flow direction of the one-way valve is the same as the flow direction of the second filter; When the oil pressure resistance of the second filter is less than the opening pressure of the one-way valve, the one-way valve is closed; when the oil pressure resistance of the second filter is greater than or equal to the opening pressure of the one-way valve, the one-way valve is opened.

11. The hydraulic device according to claim 1, characterized in that: A first filter is connected between the first oil tank and the first oil pump.

12. The hydraulic device according to claim 1, characterized in that A second solenoid valve is provided on the second oil circuit, and the inlet of the second oil pump is connected to the second oil tank; The clutch is a hydraulic clutch. The second solenoid valve is connected between the outlet of the second oil pump and the oil cylinder of the clutch and is used to control the filling and draining of oil in the oil cylinder of the clutch to achieve pressure control of the clutch.

13. The hydraulic device according to claim 12, characterized in that: The clutch includes a cylinder, an active end, and a passive end. The piston rod of the cylinder is connected to the active end, and the passive end remains stationary. The interior of the cylinder body of the cylinder is divided into a control chamber and an airtight chamber by a piston. An elastic return member is provided in the airtight chamber. One end of the elastic return member abuts against the piston of the cylinder, and the other end abuts against the inner wall of the cylinder body of the cylinder. The second solenoid valve is connected between the outlet of the second oil pump and the control chamber of the cylinder. The second oil pump fills oil into the control chamber through the second solenoid valve, which can extend the piston rod so that the active end and the driven end are combined to achieve the engagement of the clutch; the oil pressure in the control chamber is controlled by the second solenoid valve, which can adjust the engagement force between the active end and the driven end to achieve the engagement force adjustment of the clutch; the oil discharge from the control chamber is controlled by the second solenoid valve, which can retract the piston rod and separate the active end and the driven end to achieve the disengagement of the clutch.

14. The hydraulic device according to claim 12, characterized in that: The second solenoid valve is a three-position four-way valve, and the valve core of the second solenoid valve can slide and switch between a first position, a second position and a third position; When the valve core of the second solenoid valve is in the first position, the hydraulic oil flowing out of the second oil pump flows into the oil cylinder of the clutch through the second solenoid valve to achieve oil filling of the clutch; after the clutch oil filling is completed, the clutch is engaged and the valve core of the second solenoid valve is switched to the second position; When the valve core of the first solenoid valve is in the second position, the hydraulic oil flowing out of the second oil pump passes through the second solenoid valve, with a portion flowing into the oil cylinder of the clutch and the other portion flowing back to the second oil tank to adjust the pressure of the clutch; When the clutch needs to be released, the valve core of the first solenoid valve is switched to the third position, and the hydraulic oil in the oil cylinder of the clutch flows back to the second oil tank through the second solenoid valve.

15. The hydraulic device according to claim 14, characterized in that The second solenoid valve has an oil inlet, an oil outlet, a first oil return port, and a second oil return port, wherein the oil inlet and the first oil return port are located on a side of the second solenoid valve close to the second oil pump, and the oil outlet and the second oil return port are located on a side of the second solenoid valve close to the clutch; The oil inlet of the second solenoid valve is connected to the outlet of the second oil pump via a seventh pipeline, the first oil return port is connected to the second oil tank via an eighth pipeline, the oil outlet of the second solenoid valve is connected to the oil cylinder of the clutch via a ninth pipeline, and the second oil return port is connected to the second oil tank via a tenth pipeline; When the valve core of the second solenoid valve is in the first position, the oil inlet is connected to the oil outlet, and the first oil return hole is connected to the second oil return hole; When the valve core of the second solenoid valve is in the second position, the oil inlet is connected to the oil outlet and the second oil return port at the same time, and the first oil return hole is blocked; When the valve core of the second solenoid valve is located at the third position, the oil inlet is communicated with the second oil return hole, and the oil outlet is communicated with the first oil return hole.

16. The hydraulic device according to claim 15, characterized in that The tenth pipeline is provided with a sixth throttle valve, and the sixth throttle valve is used to control the amount of oil flowing back from the second oil return port to the second oil tank.

17. The hydraulic device according to claim 16, characterized in that The tenth pipeline is further provided with a third filter and a fourth filter. The third filter is connected between the second oil return port and the sixth throttle valve, and the fourth filter is connected between the sixth throttle valve and the second oil tank.

18. The hydraulic device according to claim 15, characterized in that The ninth pipeline is connected to an exhaust valve for exhausting gas from the hydraulic oil in the ninth pipeline; The pre-compression force of the exhaust valve is smaller than the KP value of the clutch.

19. The hydraulic device according to claim 15, characterized in that The ninth pipeline is connected to a pressure sensor for detecting the oil pressure in the ninth pipeline.

20. The hydraulic device according to claim 1, characterized in that A fifth filter is connected between the second oil tank and the inlet of the second oil pump; The outlet side of the filter element of the fifth filter is provided with a uniform orifice plate to separate bubbles in the hydraulic oil.

21. A hydraulic control system, characterized in that: comprising a clutch, a control unit, and the hydraulic device according to any one of claims 1 to 20, wherein the control unit is electrically connected to the first throttle valve, the first oil pump, and the second oil pump respectively; The control unit is capable of controlling the opening degree of the first throttle valve, the rotation speed of the first oil pump, and the rotation speed of the second oil pump.

22. A vehicle, characterized in that: Includes the hydraulic control system described in claim 21.

23. A control method based on the hydraulic device according to claim 1, characterized in that: include: The hydraulic oil in the first oil tank is sucked by the first oil pump and supplied to the first oil circuit to cool and lubricate the electromechanical coupling transmission; The hydraulic oil in the second oil tank is sucked by the second oil pump and supplied to the second oil circuit to control the engagement and disengagement of the clutch of the electromechanical coupling transmission; The opening of the first throttle valve is adjusted to control the amount of oil supplied from the first oil circuit to the second oil tank.

24. The control method according to claim 23, characterized in that: Also includes: Control the on / off of oil supply from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve; wherein the first solenoid valve is connected between the outlet of the first oil pump and the generator cooling oil circuit and the clutch cooling oil circuit.

25. The control method according to claim 24, characterized in that: The first solenoid valve is a three-position four-way valve, which controls the on-off of the oil supply from the first oil circuit to the generator cooling oil circuit and the clutch cooling oil circuit through the first solenoid valve. The functions include: When the vehicle is in a mode switching state, the valve core of the first solenoid valve is controlled to be in the first position, so that part of the hydraulic oil in the first oil circuit flows into the clutch cooling oil circuit and the generator cooling oil circuit respectively through the first solenoid valve; When the vehicle is in the extended-range mode or the hybrid mode, the valve core of the first solenoid valve is controlled to be in the second position, so that part of the hydraulic oil in the first oil circuit flows into the generator cooling oil circuit only through the first solenoid valve; When the vehicle is in the pure electric mode, the valve core of the first solenoid valve is controlled to be in the third position, so that the hydraulic oil in the first oil circuit is cut off at the first solenoid valve.

26. The control method according to claim 23, characterized in that: Also includes: The filling and draining of the clutch cylinder are controlled by the second solenoid valve to achieve clutch pressure control.

27. The control method according to claim 26, characterized in that: The second solenoid valve is a three-position four-way valve. The filling and draining of the clutch cylinder are controlled by the second solenoid valve, including: Controlling the valve core of the second solenoid valve to be in the first position, so that the hydraulic oil flowing out of the second oil pump flows into the oil cylinder of the clutch through the second solenoid valve to achieve oil filling of the clutch; After the clutch is filled with oil, the clutch is engaged, and the valve core of the second solenoid valve is switched to the second position, so that the hydraulic oil flowing out of the second oil pump passes through the second solenoid valve, part of which flows into the clutch cylinder and the other part flows back to the second oil tank to adjust the pressure of the clutch; Switch the valve core of the first solenoid valve to the third position, so that the hydraulic oil in the clutch cylinder flows back to the second oil tank through the second solenoid valve, thereby achieving oil release and separation of the clutch.

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