Hydraulic control system, transmission and vehicle

Abstract

The application relates to the technical field of vehicle gearboxes, and provides a hydraulic control system, a gearbox and a vehicle. The hydraulic control system comprises a double-acting pump, a first oil path connected with the double-acting pump, a first reversing valve, a first clutch branch connected with the first reversing valve, a first overflow branch provided on the first clutch branch and communicated with a first confluence branch, a first overflow valve provided on the first overflow branch, a second oil path connected with the double-acting pump, a second reversing valve, a second clutch branch connected with the second reversing valve, a second overflow branch provided on the second clutch branch and communicated with a second confluence branch, and a second overflow valve provided on the second overflow branch; and a confluence main path connected with the first confluence branch and the second confluence branch and a cooling and lubricating system. The application reduces the number of parts, lowers the cost and improves the reliability, and realizes efficient energy utilization under the premise of ensuring the independent control precision of the double clutches.

Description

Technical Field

[0001] This application relates to the field of vehicle transmission technology, and in particular to a hydraulic control system, transmission, and vehicle. Background Technology

[0002] Dual-clutch transmissions are a core component of modern automotive drivetrains, and the performance of their hydraulic control systems directly affects shift smoothness, transmission efficiency, and overall vehicle fuel consumption. This system must simultaneously achieve precise engagement and disengagement control of the clutches and provide adequate cooling and lubrication for the transmission.

[0003] Existing hydraulic control systems typically employ an architecture that separates execution and cooling functions. This means that different oil pumps are driven by independent motors: one motor is dedicated to driving the lubrication and cooling pump, providing cooling and lubrication for components such as clutches, gears, and bearings; the other two motors drive two clutch control pumps respectively, enabling independent operation of the clutches. While this multi-pump independent drive scheme achieves functional separation, it requires three or more motors and pump sets, resulting in a complex system structure, high cost, and difficulties in arranging multiple drive units within limited installation space, thus increasing the complexity of the overall vehicle layout. Utility Model Content

[0004] Based on this, the present invention provides a hydraulic control system, a transmission, and a vehicle to solve the problem of the complex structure of existing transmission hydraulic control systems.

[0005] This utility model provides a hydraulic control system, comprising: A double-acting pump with a first outlet and a second outlet; A first oil circuit is connected to the first outlet. A first directional valve is provided on the first oil circuit. The two outlets of the first directional valve are respectively connected to a first clutch branch and a first manifold branch. A first overflow branch is provided on the first clutch branch, which is connected to the first manifold branch. A first overflow valve is provided on the first overflow branch. The second oil circuit is connected to the second outlet. The second oil circuit is equipped with a second reversing valve. The two outlets of the second reversing valve are respectively connected to the second clutch branch and the second manifold branch. The second clutch branch is equipped with a second overflow branch that connects to the second manifold branch. The second overflow branch is equipped with a second overflow valve. The main busbar is connected to the cooling and lubrication system, and the ends of the first and second busbar branches are both connected to the main busbar.

[0006] In one embodiment, a first blocking valve is provided on the first bus branch, and the first overflow branch is connected between the first blocking valve and the main bus. The first blocking valve is used to block the flow of oil from the first overflow branch to the first reversing valve on the first manifold branch after the first overflow valve is opened.

[0007] In one embodiment, the first blocking valve is a one-way valve, used to open unidirectionally toward the main busbar along the first reversing valve.

[0008] In one embodiment, a second blocking valve is provided on the second bus branch, and the second overflow branch is connected between the second blocking valve and the main bus. The second shut-off valve is used to block the flow of oil from the second overflow branch to the second directional valve on the second manifold branch after the second overflow valve is opened.

[0009] In one embodiment, the second blocking valve is a one-way valve, used to open unidirectionally toward the main busbar along the second reversing valve.

[0010] In one embodiment, both the first directional valve and the second directional valve are two-position four-way directional valves controlled by electromagnetic, hydraulic, or electro-hydraulic hybrid mechanisms.

[0011] In one embodiment, the first directional valve is provided with a first return port, which is connected to the system return oil circuit. When the first directional valve switches to its first working position: the first clutch branch is connected to the first return port, and the first oil circuit is connected to the first confluence branch. The second directional valve is provided with a second return port, which is connected to the system return oil circuit. When the second directional valve switches to its first working position: the second clutch branch is connected to the second return port, and the second oil circuit is connected to the first confluence branch.

[0012] In one embodiment, the dual-acting pump has an oil suction port connected to an oil tank via a pipeline, and the pipeline is equipped with a filter.

[0013] On the other hand, the present invention also provides a transmission that includes the hydraulic control system of any of the above embodiments.

[0014] Furthermore, this utility model also provides a vehicle that includes the aforementioned transmission.

[0015] Compared with the prior art, this utility model has at least the following beneficial effects: This invention's hydraulic control system achieves efficient energy management of a dual-clutch hydraulic system through a double-acting pump and two independently controlled oil circuits. When the clutch needs to operate, the oil is directed to the clutch actuator; when the clutch is not in operation or the system has excess flow, the oil is directly directed to the cooling and lubrication system. Simultaneously, a relief valve in the system opens when the pressure exceeds a set value, diverting excess hydraulic oil into the cooling and lubrication circuit, thus recovering and utilizing energy. In this way, through intelligent allocation and energy recovery mechanisms, unnecessary energy loss is reduced, significantly lowering system energy consumption. Moreover, a single pump can handle both dual-clutch control and cooling and lubrication, reducing the number of components and energy consumption compared to an independent dual-pump solution, thereby lowering costs. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the hydraulic control system in one embodiment; Figure 2 This is a diagram of the oil flow path in the first operating mode of the hydraulic control system in one embodiment. Figure 3 This is a diagram of the oil flow path in the second operating mode of the hydraulic control system in one embodiment. Figure 4 This is a diagram of the oil flow path in the third operating mode of the hydraulic control system in one embodiment.

[0017] The reference numerals in the accompanying drawings include: 1-Double-acting pump; 101-First outlet; 102-Second outlet; 2-First oil passage; 3-Second oil passage; 4-First directional valve; 5-Second directional valve; 6-First clutch branch; 7-Second clutch branch; 8-First overflow branch; 9-First overflow valve; 10-Second manifold branch; 11-Second overflow branch; 12-Second overflow valve; 13-Second shut-off valve; 14-First shut-off valve; 15-First manifold branch; 16-Main manifold; 17-Filter; 18-Oil tank. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments.

[0019] As described in the background section, existing hydraulic control systems typically employ an architecture that separates execution and cooling functions, requiring multiple pumps to be driven independently. This results in a complex system structure, high cost, and increased complexity in the overall vehicle layout.

[0020] To address the aforementioned technical problems, this utility model provides a hydraulic control system, which includes: A double-acting pump 1 has a first outlet 101 and a second outlet 102; The first oil passage 2 is connected to the first outlet 101. The first oil passage 2 is provided with a first reversing valve 4. The two outlets of the first reversing valve 4 are respectively connected to the first clutch branch 6 and the first manifold branch 15. The first clutch branch 6 is provided with a first overflow branch 8 connected to the first manifold branch 15. The first overflow branch 8 is provided with a first overflow valve 9. The second oil passage 3 is connected to the second outlet 102. The second oil passage 3 is equipped with a second reversing valve 5. The two outlets of the second reversing valve 5 are respectively connected to the second clutch branch 7 and the second confluence branch 10. The second clutch branch 7 is equipped with a second overflow branch 11 that connects to the second confluence branch 10. The second overflow branch 11 is equipped with a second overflow valve 12. The main busbar 16 is connected to the cooling and lubrication system, and the ends of the first busbar branch 15 and the second busbar branch 10 are both connected to the main busbar 16.

[0021] This invention's hydraulic control system achieves efficient energy management of a dual-clutch hydraulic system through a double-acting pump 1 and two independently controlled oil circuits. When the clutch needs to operate, the oil is directed to the clutch actuator; when the clutch does not need to operate or the system flow is excessive, the oil is directly directed to the cooling and lubrication system. Simultaneously, a relief valve in the system opens when the pressure exceeds a set value, diverting excess hydraulic oil into the cooling and lubrication circuit, thus achieving energy recovery and utilization. In this way, through intelligent allocation and energy recovery mechanisms, unnecessary energy loss is reduced, significantly lowering system energy consumption. Moreover, a single pump can handle both dual-clutch control and cooling and lubrication, reducing the number of components and energy consumption compared to an independent dual-pump solution, thereby lowering costs.

[0022] See Figure 1 The double-acting pump 1 adopts an integrated structural design, combining the drive motor and pump body into a single, compact integrated drive unit. This structure can utilize existing integrated double-acting pump forms, such as double-acting vane pumps with integrated drive motors or similar tandem pump products. Through this integrated design, only one power source is needed to independently drive the two pumping units within the tandem pump, thereby achieving separate control of the two clutch hydraulic circuits. This not only significantly simplifies the system structure but also optimizes the overall machine's spatial layout.

[0023] It should be noted that although the double-acting pump 1 is an integrated structure, it still contains two independent hydraulic circuits. These two circuits each have independent pump chambers and flow channels, and do not interfere with each other during operation. The oil outlets of the two circuits constitute the first outlet 101 and the second outlet 102 of the double-acting pump 1, respectively.

[0024] See Figure 1The dual-acting pump 1 typically has two suction ports, each corresponding to one of the two internal hydraulic circuits. Each suction port is connected to the oil tank 18 via an inlet pipe. When the dual-acting pump 1 is running, the drive motor synchronously drives the two pumping units to work, drawing hydraulic oil from the oil tank 18, pressurizing it, and then delivering it to the first oil circuit 2 and the second oil circuit 3 through the first outlet 101 and the second outlet 102, providing the system with an independent and controllable oil source.

[0025] See Figure 1 In some embodiments, a filter 17 may be installed on the oil inlet pipe between the oil suction port and the oil tank 18. The filter 17 is used to filter out impurities in the hydraulic oil, prevent particulate contaminants from entering the hydraulic system, thereby avoiding damage to the oil pump, valves and other hydraulic components, and improving the reliability and service life of the system.

[0026] See Figure 1 In this embodiment, both the first directional valve 4 and the second directional valve 5 are two-position four-way directional valves. The four ports of the first directional valve 4 are labeled T, P, E, and F, and the four ports of the second directional valve 5 are labeled A, B, C, and D.

[0027] Please continue reading. Figure 1 In this embodiment, the P port of the first reversing valve 4 is connected to the first oil circuit 2, the T port is the first return oil port connected to the system return oil circuit, the E port is connected to the first clutch branch 6, and the F port is connected to the first manifold branch 15.

[0028] Based on this oil circuit design, the first directional valve 4 has two operating states: like Figure 2 As shown, when the first directional valve 4 switches to the left position, the P port is connected to the E port, and the F port is connected to the T port. At this time, the pressure oil in the first oil circuit 2 enters the first clutch branch 6 through the PE oil circuit of the first directional valve 4, pushing the first clutch to engage; at the same time, the first manifold branch 15 is connected to the return oil circuit through the FT oil circuit of the first directional valve 4.

[0029] like Figure 3 As shown, when the first directional valve 4 switches to the right position (the first working position of the first directional valve 4), the P port and F port are connected, and the E port and T port are connected simultaneously. At this time, the pressure oil in the first oil circuit 2 enters the first manifold branch 15 through the PF oil circuit of the first directional valve 4, and finally flows to the cooling and lubrication system; while the oil in the first clutch branch 6 flows back to the oil tank 18 through the ET oil circuit of the first directional valve 4, and the first clutch is unloaded and disconnected under the action of the reset device.

[0030] Please continue reading. Figure 1In this embodiment, port B of the second reversing valve 5 is connected to the second oil circuit 3, port A is the second return oil port connected to the system return oil circuit, port D is connected to the second clutch branch 7, and port C is connected to the second manifold branch 10.

[0031] Based on this oil circuit design, the second directional valve 5 has two operating states: like Figure 3 As shown, when the second directional valve 5 switches to the right position, ports B and D are connected, and ports A and C are also connected. At this time, the pressure oil in the second oil circuit 3 enters the second clutch branch 7 through the BD oil circuit of the second directional valve 5, pushing the second clutch to engage; at the same time, the second manifold branch 10 is connected to the return oil circuit through the AC oil circuit of the second directional valve 5.

[0032] like Figure 2 As shown, when the second directional valve 5 switches to the left position (the first working position of the second directional valve 5), ports B and C are connected, and ports A and D are connected simultaneously. At this time, the pressurized oil in the second oil circuit 3 enters the second manifold branch 10 through the BC oil circuit of the second directional valve 5, and finally flows to the cooling and lubrication system; while the oil in the second clutch branch 7 flows back to the oil tank 18 through the AD oil circuit of the second directional valve 5, and the second clutch is unloaded and disconnected under the action of the reset device.

[0033] Furthermore, in this embodiment, the specific control methods for the first reversing valve 4 and the second reversing valve 5 can be electromagnetic control, hydraulic control, or electro-hydraulic composite control.

[0034] In this embodiment, the ends of the first clutch branch 6 and the second clutch branch 7 are respectively connected to the actuators of the first clutch and the second clutch. Specifically, each branch is typically connected to the corresponding hydraulic cylinder or piston chamber of the clutch. By injecting and releasing pressurized oil in the hydraulic circuit, the actuator is driven to operate, thereby achieving the engagement and disengagement of the corresponding clutch. The clutch actuator and its connection method with the hydraulic branch involved in this part are conventional and mature technologies in the field. Their specific structure and working principle are well known to those skilled in the art, and therefore will not be described in detail here.

[0035] In this embodiment, the first overflow branch 8 is used to guide the oil exceeding the set pressure in the first clutch branch 6 to the first confluence branch 15, and finally deliver it to the cooling and lubrication system through the main confluence branch 16, thereby providing cooling and lubrication for the system components.

[0036] The specific work process is as follows: Figure 2As shown, the first pump delivers pressurized oil to the first clutch branch 6, and the oil enters the piston chamber of the first clutch and builds up pressure. When the oil pressure reaches a level sufficient to drive the first clutch to engage, the pressure in the first clutch branch 6 continues to rise. When the oil pressure reaches the preset opening pressure of the first relief valve 9, the first relief valve 9 opens. At this time, the excess oil continuously output by the first pump flows into the first manifold branch 15 through the first relief branch 8, and finally into the cooling and lubrication system for utilization, realizing an effective combination of energy recovery and system cooling and lubrication.

[0037] In this embodiment, the function of the second overflow branch 11 corresponds to that of the first overflow branch 8. It is used to guide the oil in the second clutch branch 7 that exceeds the set pressure to the second confluence branch 10, and finally deliver it to the cooling and lubrication system through the main confluence branch 16 to provide continuous cooling and lubrication for the transmission.

[0038] The opening of the second relief valve 12 depends entirely on the oil pressure of the second clutch branch 7 itself. For example... Figure 3 As shown, when the oil pressure in this branch reaches the preset value of the second relief valve 12, the valve port opens, allowing excess pressure oil to enter the confluence branch through the second relief branch 11, thereby ensuring precise pressure control of the second clutch while achieving efficient reuse of hydraulic energy.

[0039] In this embodiment, the opening pressures of the first relief valve 9 and the second relief valve 12 can be set and adjusted independently. This allows the system to configure relief pressure values ​​that match the actual working characteristics and execution pressure requirements of different clutches. For example, if the first clutch requires a higher execution pressure, the opening pressure of the first relief valve 9 can be increased accordingly; while if the second clutch needs to operate at a lower pressure, the opening pressure of the second relief valve 12 can be independently set to a lower value.

[0040] Further, see Figure 1 A first shut-off valve 14 is also provided on the first manifold branch 15. The first overflow branch 8 is connected downstream of the first shut-off valve 14, that is, the pipeline section connecting the first shut-off valve 14 and the main manifold 16. The main function of the first shut-off valve 14 is to block the backflow of oil upstream (i.e., towards the first directional valve 4) when the first overflow valve 9 is opened and oil flows into the first manifold branch 15 through the first overflow branch 8. By setting the first shut-off valve 14, the oil output from the first overflow branch 8 can be effectively prevented from flowing back to the T port of the first directional valve 4 through the first manifold branch 15, thereby ensuring that all overflow oil can be directionally delivered to the cooling and lubrication system, ensuring the stability and reliability of the system's cooling and lubrication.

[0041] In this embodiment, the first blocking valve 14 is preferably a one-way valve. The one-way valve is configured to open from the first reversing valve 4 toward the main flow path 16, and close in the opposite direction. This design can automatically realize the forward flow and reverse cut-off of oil without external control, ensuring the smooth flow of the first flow path 15 under normal operating conditions, and effectively preventing backflow of oil. It has a simple structure and reliable operation.

[0042] In some alternative embodiments, the first shut-off valve 14 may also be an electromagnetically controlled switching valve, such as a two-position two-way solenoid valve. In this configuration, the system can actively control the clutch based on its operating state: when the first clutch does not need to engage, the switching valve is opened to allow the first manifold 15 to flow freely; when the first clutch needs to engage, the switching valve is closed to block the passage, thus avoiding interference with clutch pressure build-up.

[0043] See Figure 1 A second shut-off valve 13 is correspondingly provided on the second manifold branch 10. The second overflow branch 11 is connected downstream of the second shut-off valve 13, that is, the pipeline section connecting the second shut-off valve 13 and the main manifold 16. The main function of the second shut-off valve 13 is to effectively block the flow of oil upstream (i.e., towards the second directional valve 5) when the second overflow valve 12 is opened and pressurized oil flows into the second manifold branch 10 through the second overflow branch 11. By setting the second shut-off valve 13, it can be ensured that all oil flowing out of the second overflow branch 11 is directed to the cooling and lubrication system, effectively preventing it from flowing back to the return port of the second directional valve 5 through the second manifold branch 10, thereby ensuring a stable supply of cooling and lubrication to the system.

[0044] Similarly, in this embodiment, the second shut-off valve 13 can preferably be a one-way valve. The installation direction of this one-way valve allows oil to flow from the second directional valve 5 towards the main manifold 16, while automatically shutting it off in the opposite direction. This design achieves one-way flow without external control, and its structure is simple and reliable.

[0045] Alternatively, the second shut-off valve 13 can also be an electromagnetically controlled on / off valve (such as a two-position two-way solenoid valve). In this configuration, the valve port can be controlled by an electrical signal: when the second clutch does not need to work, the valve is opened; when the second clutch needs to build pressure, the valve is closed to avoid interference from the manifold to the clutch operation.

[0046] The working principle of the hydraulic control system in this embodiment will be explained in detail below, taking into account three typical working modes: Operating mode 1: First clutch engaged, second clutch disengaged, system requires cooling and lubrication. The drive motor starts, which drives the double-acting pump 1 to work.

[0047] like Figure 2 As shown, the pressurized oil output from the first pump is delivered to the first directional valve 4 via the first oil circuit 2. At this time, the first directional valve 4 is energized and switched to the left position, with its P port connected to its E port. The pressurized oil enters the first clutch branch 6, pushing the first clutch to engage. When the oil pressure continues to rise to the opening pressure of the first relief valve 9, the valve opens, and the excess oil output from the first pump enters the first manifold branch 15 via the first relief branch 8, eventually flowing into the cooling and lubrication system.

[0048] The pressurized oil output from the second pump is delivered to the second directional valve 5 via the second oil circuit 3. At this time, the second directional valve 5 is de-energized and in the left position, with its B port connected to its C port. The pressurized oil directly enters the second manifold branch 10 and flows to the cooling and lubrication system. At the same time, its A port is connected to its D port, so that the second clutch branch 7 is connected to the return oil circuit, and the second clutch is unloaded and remains disconnected.

[0049] In this mode: the output energy of the first pump is mainly used to drive the first clutch, and the surplus is used for cooling and lubrication; the output energy of the second pump is used entirely for cooling and lubrication.

[0050] Operating mode two: First clutch disengaged, second clutch engaged, system requires cooling and lubrication. The drive motor starts, which drives the double-acting pump 1 to work.

[0051] like Figure 3 As shown, the pressurized oil output from the first pump is delivered to the first directional valve 4 via the first oil circuit 2. At this time, the first directional valve 4 is de-energized and in the right position, with its P port connected to its F port, and the pressurized oil directly enters the first manifold branch 15 and flows to the cooling and lubrication system; at the same time, its E port is connected to its T port, so that the first clutch branch 6 is connected to the return oil circuit, and the first clutch is unloaded and remains disconnected.

[0052] The pressurized oil output from the second pump is delivered to the second directional valve 5 via the second oil circuit 3. At this time, the second directional valve 5 is energized and switched to the right position, with its B port connected to its D port. The pressurized oil enters the second clutch branch 7, pushing the second clutch to engage. When the oil pressure continues to rise to the opening pressure of the second relief valve 12, the valve opens, and the excess oil output from the second pump enters the second manifold branch 10 via the second relief branch 11, eventually flowing into the cooling and lubrication system.

[0053] In this mode: the output energy of the second pump is mainly used to drive the second clutch, and the surplus is used for cooling and lubrication; the output energy of the first pump is used entirely for cooling and lubrication.

[0054] Operating Mode 3: First clutch engaged, second clutch engaged The drive motor starts, which drives the double-acting pump 1 to work.

[0055] like Figure 4As shown, the pressurized oil output from the first pump passes through the first oil circuit 2 to the first directional valve 4 (energized, left position), and enters the first clutch branch 6 to drive the first clutch to engage. Excess oil passes through the open first overflow valve 9 and enters the cooling and lubrication system via the first overflow branch 8.

[0056] The pressurized oil output from the second pump flows through the second oil circuit 3 to the second directional valve 5 (energized, right position), and then enters the second clutch branch 7 to engage the second clutch. Excess oil flows through the open second overflow valve 12 and into the cooling and lubrication system via the second overflow branch 11.

[0057] In this mode: both pumps work simultaneously, driving the two clutches respectively, and the surplus oil from both pumps jointly provides oil to the cooling and lubrication system.

[0058] On the other hand, this utility model embodiment also provides a transmission that includes the hydraulic control system of any of the above embodiments.

[0059] In another aspect, this utility model embodiment also provides a vehicle that includes the aforementioned transmission.

[0060] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0061] It should be noted that the illustrations provided in this embodiment are merely schematic representations of the basic concept of this utility model. The structures, proportions, sizes, etc., depicted in the accompanying drawings are only for illustrative purposes to aid those skilled in the art and to enable them to understand and read the content disclosed herein. They are not intended to limit the implementation conditions of this utility model. Any modifications to the structure, changes in proportions, or adjustments to the size, without affecting the effects and objectives achieved by this utility model, should still fall within the scope of the technical content disclosed herein.

[0062] The orientations or positional relationships indicated by terms such as "upper," "lower," "left," "right," "middle," "longitudinal," "transverse," "horizontal," "inner," "outer," "radial," and "circumferential" used in this specification are based on the orientations or positional relationships shown in the accompanying drawings and are only for the purpose of simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

Claims

1. A hydraulic control system, characterized in that, include: A double-acting pump (1) has a first outlet (101) and a second outlet (102); The first oil circuit (2) is connected to the first outlet (101). The first oil circuit (2) is provided with a first reversing valve (4). The two outlets of the first reversing valve (4) are respectively connected to the first clutch branch (6) and the first confluence branch (15). The first clutch branch (6) is provided with a first overflow branch (8) connected to the first confluence branch (15). The first overflow branch (8) is provided with a first overflow valve (9). The second oil passage (3) is connected to the second outlet (102). The second oil passage (3) is provided with a second reversing valve (5). The two outlets of the second reversing valve (5) are respectively connected to the second clutch branch (7) and the second confluence branch (10). The second clutch branch (7) is provided with a second overflow branch (11) connected to the second confluence branch (10). The second overflow branch (11) is provided with a second overflow valve (12). The main busbar (16) is connected to the cooling and lubrication system, and the ends of the first busbar branch (15) and the second busbar branch (10) are both connected to the main busbar (16).

2. The hydraulic control system according to claim 1, characterized in that, The first bus branch (15) is provided with a first shut-off valve (14), and the first overflow branch (8) is connected between the first shut-off valve (14) and the main bus branch (16); The first blocking valve (14) is used to block the flow of oil from the first overflow branch (8) to the first reversing valve (4) on the first manifold branch (15) after the first overflow valve (9) is opened.

3. The hydraulic control system according to claim 2, characterized in that, The first blocking valve (14) is a one-way valve, used to open unidirectionally along the first reversing valve (4) toward the main busbar (16).

4. The hydraulic control system according to claim 1, characterized in that, The second bus branch (10) is provided with a second shut-off valve (13), and the second overflow branch (11) is connected between the second shut-off valve (13) and the main bus branch (16); The second blocking valve (13) is used to block the flow of oil from the second overflow branch (11) to the second reversing valve (5) on the second manifold branch (10) after the second overflow valve (12) is opened.

5. The hydraulic control system according to claim 4, characterized in that, The second blocking valve (13) is a one-way valve, used to open unidirectionally along the second reversing valve (5) toward the main busbar (16).

6. The hydraulic control system according to claim 1, characterized in that, Both the first reversing valve (4) and the second reversing valve (5) are two-position four-way reversing valves controlled by electromagnetic, hydraulic or electro-hydraulic hybrid methods.

7. The hydraulic control system according to claim 6, characterized in that, The first reversing valve (4) is provided with a first return oil port, which is connected to the system return oil circuit. When the first reversing valve (4) is switched to its first working position: the first clutch branch (6) is connected to the first return oil port, and the first oil circuit (2) is connected to the first confluence branch (15). The second reversing valve (5) is provided with a second return port, which is connected to the system return oil circuit. When the second reversing valve (5) switches to its first working position: the second clutch branch (7) is connected to the second return port, and the second oil circuit (3) is connected to the first confluence branch (15).

8. The hydraulic control system according to claim 1, characterized in that, The double-acting pump (1) has an oil suction port, which is connected to the oil tank (18) via a pipeline, and a filter (17) is installed on the pipeline.

9. A transmission, characterized in that, Including the hydraulic control system as described in any one of claims 1-8.

10. A vehicle, characterized in that, Including the transmission as described in claim 9.

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