Hydraulic control system and method for clutch

Abstract

According to the hydraulic control system and method for the clutch, one end of a first lubricating oil pump (1) is connected with a lubricating oil tank, and the other end of the first lubricating oil pump (1) is connected with the input end of a pressure regulating valve (11) and the input end of a first electromagnetic operating valve (9); the first output end of the first electromagnetic operating valve (9) is connected with the first input end of the second electromagnetic operating valve (10), and the second output end of the first electromagnetic operating valve (9) is connected with the second input end of the second electromagnetic operating valve (10), one end of the first ball valve (13), one end of the third ball valve (16) and the first input end of the electro-hydraulic proportional valve (12). A third output end of the first electromagnetic operating valve (9) is connected with a second input end of the electro-hydraulic proportional valve (12); the output end of the electro-hydraulic proportional valve (12), the other end of the third ball valve (16) and the output end of the second electromagnetic operating valve (10) are connected in parallel and then connected with the feedback end of the pressure regulating valve (11).

Description

Technical Field

[0001] The present invention relates to the technical field of clutches, and in particular to a hydraulic control system and method for a clutch. Background Art

[0002] The wet multi-plate friction clutch (hereinafter referred to as the clutch) is one of the important transmission components in the power transmission system. It is usually integrated in the gearbox to complete the connection, separation and reversing functions between the main engine and the propeller. During the clutch connection process, the propeller shaft at the driven end needs to be brought from zero speed or even in the opposite direction to the speed corresponding to the main engine operation. During this period, from the perspective of the entire propulsion system, due to the need to overcome the large rotational inertia of the propeller shaft, the system vibration and impact are relatively large, and the main engine usually experiences stalling and speed reduction.

[0003] At present, the research and development of domestic clutches and the basic research and even practical application of clutch control application technology are obviously insufficient. The technical level of high-speed, high-power density wet friction clutches is far behind that of well-known foreign brands in terms of structural richness, power density, and process level. There is a lack of basic research on the oil groove of the friction plate, the pressure, clearance, lubrication of the friction pair, and clutch connection and separation control. Summary of the invention

[0004] In view of the technical problem in the prior art that the large rotational inertia of the driven-end propeller shaft leads to a large impact, the present invention provides a hydraulic control system and method for a clutch, which realizes the relative sliding friction of the clutch friction plate in the initial stage of engagement by controlling the rising curve of the clutch working oil pressure, thereby avoiding the displacement impact when the propeller shaft system has a large rotational inertia, greatly improving the reliability of the gearbox and the stability of the ship during operation.

[0005] In order to achieve the above object, the present invention provides the following technical solutions:

[0006] A hydraulic control system for a clutch, comprising a first lubricating oil pump 1, a pressure regulating valve 11, a first electromagnetic control valve 9, a second electromagnetic control valve 10, an electro-hydraulic proportional valve 12, a first ball valve 13, and a third ball valve 16;

[0007] One end of the first lubricating oil pump 1 is connected to the lubricating oil tank, and the other end of the first lubricating oil pump 1 is connected to the input end of the pressure regulating valve 11 and the input end of the first electromagnetic control valve 9; the first output end of the first electromagnetic control valve 9 is connected to the first input end of the second electromagnetic control valve 10, and the second output end of the first electromagnetic control valve 9 is respectively connected to the second input end of the second electromagnetic control valve 10, one end of the first ball valve 13, one end of the third ball valve 16, and the first input end of the electro-hydraulic proportional valve 12, and the third output end of the first electromagnetic control valve 9 is connected to the second input end of the electro-hydraulic proportional valve 12;

[0008] The output end of the electro-hydraulic proportional valve 12 , the other end of the third ball valve 16 , and the output end of the second electromagnetic control valve 10 are connected in parallel to the feedback end of the pressure regulating valve 11 .

[0009] Preferably, it also includes a second ball valve 14; the first output end of the pressure regulating valve 11 is connected to one end of the clutch 15, the other end of the clutch 15 is respectively connected to the other end of the first ball valve 13 and one end of the second ball valve 14, the other end of the second ball valve 14 is connected to the third input end of the electro-hydraulic proportional valve 12; the second output end of the pressure regulating valve 11 is connected to the lubricating oil tank.

[0010] Preferably, a cooler 6 and a filter 7 are sequentially arranged between the first lubricating oil pump 1 and the pressure regulating valve 11 .

[0011] Preferably, a one-way valve 3 and a throttle valve 5 are provided between the first lubricating oil pump 1 and the cooler 6 .

[0012] Preferably, a safety valve 4 is also provided directly between the throttle valve 5 and the lubricating oil tank.

[0013] Preferably, an oil filter 8 is further provided between the filter 7 and the first electromagnetic control valve 9 .

[0014] Preferably, a first pressure sensor, a temperature sensor, a relief valve, a lubricating bearing, and a lubricating gear are further provided between the pressure regulating valve 11 and the clutch 15 .

[0015] The present invention also provides a hydraulic control method for a clutch, which specifically includes a first control method:

[0016] First, open the first ball valve 13, and simultaneously close the second ball valve 14, the third ball valve 16, and the electro-hydraulic proportional valve 12;

[0017] Then, the first lubricating oil pump 1 is started, and the lubricating oil passes through the first lubricating oil pump 1 from the lubricating oil tank to the pressure regulating valve 11. At this time, the first electromagnetic control valve 9 and the second electromagnetic control valve 10 perform the first interlocking control action, and the pressure gradually increases to reach the stable torque transmission stage of the clutch, completing the whole process of soft clutch shifting.

[0018] Preferably, a second control method is also included:

[0019] First, open the second ball valve 14, the third ball valve 16, and the electro-hydraulic proportional valve 12, and close the first ball valve 13;

[0020] Then, the first oil pump 1 is started, and the lubricating oil passes through the first oil pump 1 from the oil tank to the pressure regulating valve 11. At this time, the first solenoid control valve 9 and the electro-hydraulic proportional valve 12 perform the second interlocking control action, and the oil pressure rises linearly from 0 until the clutch reaches stable torque transmission, completing the soft shifting of the clutch.

[0021] Preferably, a third control method is also included:

[0022] First, open the first ball valve 13 and the electro-hydraulic proportional valve 12, and close the second ball valve 14 and the third ball valve 16;

[0023] Then, the first lubricating oil pump 1 is started, and the lubricating oil passes through the first lubricating oil pump 1 from the lubricating oil tank to the pressure regulating valve 11. At this time, the first solenoid control valve 9 and the electro-hydraulic proportional valve 12 perform the third interlocking control action, and the oil pressure rises linearly until the clutch reaches stable torque transmission and the clutch soft shift is completed.

[0024] In summary, due to the adoption of the above technical solution, compared with the prior art, the present invention has at least the following beneficial effects:

[0025] 1. The present invention realizes the regulation of oil pressure through three different methods, and the principle of realizing the oil pressure rising curve of each method is different.

[0026] 2. The present invention adopts a control box to control the interlocking of three solenoid valves. By adjusting the interlocking mode on the control box, the interlocking of the first solenoid control valve 9 and the second solenoid control valve 10, and the interlocking of the first solenoid control valve 9 and the electro-hydraulic proportional valve 12 are realized, so as to more accurately control the rising time of the oil pressure curve.

[0027] 3. In the three methods of the present invention, the oil pressure rise time is adjustable, and the soft connection time can be adjusted according to the sliding condition of the friction plate. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 A hydraulic control system for a clutch and a schematic diagram of its principle according to an exemplary embodiment 1 of the present invention.

[0029] Figure 2 Schematic diagram of a hydraulic control method for a clutch according to exemplary embodiment 3 of the present invention.

[0030] Figure 3 Schematic diagram of a hydraulic control system for a clutch according to an exemplary embodiment 4 of the present invention.

[0031] Figure 4 Schematic diagram of an oil pressure rise curve according to exemplary embodiment 4 of the present invention. DETAILED DESCRIPTION

[0032] The present invention is further described in detail below in conjunction with the examples and specific implementation methods. However, this should not be understood as the scope of the above subject matter of the present invention being limited to the following examples, and all technologies realized based on the content of the present invention belong to the scope of the present invention.

[0033] In the description of the present invention, it is necessary to understand that the terms "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0034] Example 1

[0035] like Figure 1 As shown, the present invention provides a hydraulic control system for a clutch, including a first lubricating oil pump 1, a second lubricating oil pump 2, a cooler 6, a filter 7, a secondary pressure regulating valve 11, a first electromagnetic control valve 9, a second electromagnetic control valve 10, an electro-hydraulic proportional valve 12, a first ball valve 13, a second ball valve 14, a third ball valve 16, a first pressure sensor P1, a second pressure sensor P2, a third pressure sensor P3, a fourth pressure sensor P4, a fifth pressure sensor P5, and a temperature sensor T.

[0036] In this embodiment, one end of the first lubricating oil pump 1 and one end of the second lubricating oil pump 2 (the first lubricating oil pump 1 is a machine-driven lubricating oil pump, which is connected to the gearbox rotating shaft to realize oil suction; the second lubricating oil pump 2 is an electric lubricating oil standby pump, which is driven by its own motor to realize oil suction, as a standby, the second lubricating oil pump 2 is started only when the first lubricating oil pump 1 is damaged) are respectively connected to the lubricating oil tank, and the other end of the first lubricating oil pump 1 and the other end of the second lubricating oil pump 2 are connected in parallel and then sequentially pass through the cooler 6 and the filter 7 and are respectively connected to the first end of the secondary pressure regulating valve 11 and the input end of the first electromagnetic control valve 9; the first output end of the first electromagnetic control valve 9 is connected to the first input end of the second electromagnetic control valve 10, the second output end of the first electromagnetic control valve 9 is respectively connected to the second input end of the second electromagnetic control valve 10, one end of the first ball valve 13, one end of the third ball valve 16, and the first input end of the electro-hydraulic proportional valve 12, and the third output end of the first electromagnetic control valve 9 is connected to the second input end of the electro-hydraulic proportional valve 12;

[0037] The output end of the electro-hydraulic proportional valve 12, the other end of the third ball valve 16, and the output end of the second electromagnetic control valve 10 are connected in parallel to the feedback end of the secondary pressure regulating valve 11;

[0038] The first output end of the secondary pressure regulating valve 11 is connected to one end of the clutch 15, the other end of the clutch 15 is respectively connected to the other end of the first ball valve 13 and one end of the second ball valve 14, the other end of the second ball valve 14 is connected to the third input end of the electro-hydraulic proportional valve 12; the second output end of the secondary pressure regulating valve 11 is connected to the lubricating oil tank.

[0039] In this embodiment, a one-way valve 3 and a throttle valve 5 are further provided between the first lubricating oil pump 1 or the second lubricating oil pump 2 and the cooler 6; wherein, the function of the one-way valve 3 is to allow oil to flow in one direction only, that is, the oil flows in the direction of the throttle valve 5 after being sucked out from the first lubricating oil pump 1, and will not flow to the second lubricating oil pump 2; the function of the throttle valve 5 is to adjust the amount of lubricating oil flow in the lubricating oil tank.

[0040] In this embodiment, a safety valve 4 is also provided directly between the throttle valve 5 and the lubricating oil tank; the safety valve 4 is opened to release the pressure when the lubricating oil pressure is too high (>2.5 MPa).

[0041] In this embodiment, an oil filter 8 is further provided between the filter 7 and the first electromagnetic control valve 9; the function of the oil filter 8 is to filter impurities in the oil.

[0042] In this embodiment, a first pressure sensor P1, a temperature sensor T, a relief valve, a lubricating bearing, a lubricating gear, etc. are also provided between the secondary pressure regulating valve 11 and the clutch 15. The relief valve, the lubricating bearing, and the lubricating gear are parts requiring oil.

[0043] In this embodiment, a second pressure sensor P2 is further provided between the filter 7 and the secondary pressure regulating valve 11 .

[0044] In this embodiment, a third pressure sensor P3 is further provided between the feedback end of the secondary pressure regulating valve 11 and the second electromagnetic control valve 10 .

[0045] In this embodiment, a fourth pressure sensor P4 is further provided between the clutch 15 and the second ball valve 14 .

[0046] In this embodiment, a fifth pressure sensor P5 is further provided between the electro-hydraulic proportional valve 12 and the second ball valve 14 .

[0047] Based on the above-mentioned hydraulic control system for a clutch, the present invention further provides a hydraulic control method for a clutch, which specifically includes the following steps:

[0048] like Figure 1 As shown in the figure, the black arrow indicates the direction of oil circuit operation, the solid line indicates that the oil circuit is unobstructed, and the dotted line indicates that the oil circuit is blocked.

[0049] First, when the first interlock is selected, the oil pressure curve b can be realized; the first ball valve 13 is opened, and the second ball valve 14, the third ball valve 16, and the electro-hydraulic proportional valve 12 are closed at the same time;

[0050] Then, the first lubricating oil pump 1 or the second lubricating oil pump 2 is started, and the lubricating oil from the lubricating oil tank passes through the first lubricating oil pump 1 or the second lubricating oil pump 2, the cooler 6, and the filter 7 in sequence to reach the secondary pressure regulating valve 11. At this time, the first electromagnetic control valve 9 and the second electromagnetic control valve 10 perform the first interlocking control action (the selection of the interlocking control action can be controlled by the gear box monitor), and the pressure gradually increases and starts to increase pressure to reach the stable torque transmission stage of the clutch, completing the whole process of soft clutch shifting, and realizing the oil pressure curve b, as shown in FIG. Figure 4 shown.

[0051] The conventional clutch engagement adopts curve a, the oil pressure rises quickly, and the clutch completes the engagement in a short time, which cannot meet the occasions that require soft engagement; curve b keeps the transmission torque of the clutch slip basically unchanged during the engagement process, but the resistance of the stern shaft gradually increases with the increase of speed, so the acceleration of the shaft system gradually decreases, which will prolong the clutch slip process.

[0052] The first interlocking control action is: the first solenoid control valve 9 and the second solenoid control valve 10 are controlled by the monitoring instrument of the gear box at the same time, and there is a logical relationship between the first solenoid control valve 9 and the second solenoid control valve 10, that is, after the first solenoid valve 9 is started, the lubricating oil pressure maintains a relatively low oil pressure value t1 time (because of the existence of the secondary pressure regulating valve 11, the feedback oil circuit is blocked at this time, that is, there is no input at the feedback end, and the oil pressure is not established, it is only the initial lubricating oil pressure, at this time the clutch friction plate slips, thereby overcoming the rotational inertia of the propeller), when the delay time t1 of the second solenoid control valve 10 is reached (the delay time can be set and adjusted as needed, adjustable from 1 to 20 seconds), after the second solenoid control valve 10 is actuated, the lubricating oil pressure reaches the feedback end of the pressure regulating valve 11 through the feedback oil circuit, so that the working oil pressure of the clutch 15 increases.

[0053] The principle of increasing working oil pressure is: the pressure regulating valve 11 is a two-stage pressure regulating valve. If the pressure is to be increased, the internal valve core of the two-stage pressure regulating valve 11 needs to be moved to reduce the lubricating oil inlet. If the flow rate remains unchanged, the pressure will be held up. When the second solenoid control valve 10 is actuated, a feedback oil circuit will form a passage at this time. The oil pressure at the feedback end will push the internal valve core of the two-stage pressure regulating valve 11 to move, causing the lubricating oil inlet to become smaller, and the lubricating oil pressure will increase.

[0054] Example 2

[0055] Based on the hydraulic control system for a clutch described in Example 1, the present invention further provides a hydraulic control method for a clutch, which specifically includes the following steps:

[0056] like Figure 2 As shown in the figure, the black arrow indicates the direction of oil circuit operation, the solid line indicates that the oil circuit is unobstructed, and the dotted line indicates that the oil circuit is blocked.

[0057] First, when the second interlock is selected, the oil pressure curve d can be realized; the second ball valve 14, the third ball valve 16, and the electro-hydraulic proportional valve 12 are opened, and the first ball valve 13 is closed at the same time;

[0058] Then, the first lubricating oil pump 1 or the second lubricating oil pump 2 is started, and the lubricating oil from the lubricating oil tank passes through the first lubricating oil pump 1 or the second lubricating oil pump 2, the cooler 6, and the filter 7 in sequence to reach the secondary pressure regulating valve 11. At this time, the first electromagnetic control valve 9 and the electro-hydraulic proportional valve 12 perform the second interlocking control action. According to the oil pressure rise time set in the electro-hydraulic proportional valve 12, the working oil pressure rises linearly until the clutch reaches stable torque transmission, the clutch soft engagement is completed, and the oil pressure curve d is realized, as shown in FIG. Figure 4 shown.

[0059] In the oil pressure curve d, the transmission torque of the clutch slip gradually increases during the shifting process, and the stern shaft acceleration does not gradually slow down as in curve b, which is consistent with the fact that the main engine's power increases significantly when the speed increases.

[0060] The second interlocking control action is: the first solenoid control valve 9 and the electro-hydraulic proportional valve 12 are controlled by the monitoring instrument of the gear box at the same time, and there is a logical relationship between the first solenoid control valve 9 and the second electro-hydraulic proportional valve 12; that is, the first solenoid valve 9 is started first (the electro-hydraulic proportional valve 12 has not been started yet), and since the first ball valve 13 is closed, the pressure at the fourth pressure sensor P4 is 0; when the oil pressure rising time t2 of the electro-hydraulic proportional valve 12 is reached (the oil pressure rising time can be set and adjusted as needed, and can be adjusted from 10 to 15 seconds), the electro-hydraulic proportional valve 12 is actuated, and the lubricating oil pressure reaches the feedback end of the pressure regulating valve 11 through the feedback oil circuit, so that the working oil pressure of the clutch 15 (the pressure at the fourth pressure sensor P4) increases linearly from 0.

[0061] Example 3

[0062] Based on the hydraulic control system for a clutch described in Example 1, the present invention further provides a hydraulic control method for a clutch, which specifically includes the following steps:

[0063] like Figure 3 As shown in the figure, the black arrow indicates the direction of oil circuit operation, the solid line indicates that the oil circuit is unobstructed, and the dotted line indicates that the oil circuit is blocked.

[0064] First, when the second interlock is selected, the oil pressure curve c can be realized; the first ball valve 13 and the electro-hydraulic proportional valve 12 are opened, and the second ball valve 14 and the third ball valve 16 are closed at the same time;

[0065] Then, the first lubricating oil pump 1 or the second lubricating oil pump 2 is started, and the lubricating oil from the lubricating oil tank passes through the first lubricating oil pump 1 or the second lubricating oil pump 2, the cooler 6, and the filter 7 in sequence to reach the secondary pressure regulating valve 11. At this time, the first electromagnetic control valve 9 and the electro-hydraulic proportional valve 12 perform the third interlocking control action, and the working oil pressure of the secondary pressure regulating valve 11 maintains a low pressure for t2 time, and then the oil pressure rises linearly until the clutch transmits torque stably, the clutch soft shifting time is completed, and the oil pressure curve c is realized, as shown in FIG. Figure 4 shown.

[0066] In the oil pressure curve c, the transmission torque of the clutch slip gradually increases during the shifting process, and the stern shaft acceleration does not gradually slow down as in curve b, which is consistent with the fact that the main engine's power increases significantly when the speed increases.

[0067] The third interlocking control action is: the first solenoid control valve 9 and the electro-hydraulic proportional valve 12 are controlled by the monitoring instrument of the gear box at the same time, and there is a logical relationship between the first solenoid control valve 9 and the second electro-hydraulic proportional valve 12, that is, after the first solenoid valve 9 is started, the lubricating oil pressure maintains a relatively low oil pressure value for t2 time (because of the existence of the secondary pressure regulating valve 11, the feedback oil circuit is blocked at this time, that is, there is no input at the feedback end, and the oil pressure is not established. The pressure at the fourth pressure sensor P4 is the initial lubricating oil pressure. At this time, the clutch friction plate slips, thereby overcoming the rotational inertia of the propeller). When the oil pressure rise time t2 of the electro-hydraulic proportional valve 12 is reached (the oil pressure rise time can be set and adjusted as needed, and can be adjusted from 10 to 15 seconds), the electro-hydraulic proportional valve 12 is actuated, and the lubricating oil pressure reaches the feedback end of the pressure regulating valve 11 through the feedback oil circuit, so that the working oil pressure of the clutch 15 increases linearly from the initial lubricating oil pressure.

[0068] Those skilled in the art will appreciate that the above-mentioned embodiments are specific examples for implementing the present invention, and in actual applications, various changes may be made thereto in form and detail without departing from the spirit and scope of the present invention.

Claims

1. A hydraulic control system for a clutch, characterized in that: It comprises a first lubricating oil pump (1), a pressure regulating valve (11), a first electromagnetic control valve (9), a second electromagnetic control valve (10), an electro-hydraulic proportional valve (12), a first ball valve (13), and a third ball valve (16); One end of the first lubricating oil pump (1) is connected to the lubricating oil tank, and the other end of the first lubricating oil pump (1) is connected to the input end of the pressure regulating valve (11) and the input end of the first electromagnetic control valve (9); the first output end of the first electromagnetic control valve (9) is connected to the first input end of the second electromagnetic control valve (10), the second output end of the first electromagnetic control valve (9) is respectively connected to the second input end of the second electromagnetic control valve (10), one end of the first ball valve (13), one end of the third ball valve (16), and the first input end of the electro-hydraulic proportional valve (12), and the third output end of the first electromagnetic control valve (9) is connected to the second input end of the electro-hydraulic proportional valve (12); The output end of the electro-hydraulic proportional valve (12), the other end of the third ball valve (16), and the output end of the second electromagnetic control valve (10) are connected in parallel and then connected to the feedback end of the pressure regulating valve (11).

2. A hydraulic control system for a clutch as claimed in claim 1, characterized in that: It also includes a second ball valve (14); the first output end of the pressure regulating valve (11) is connected to one end of the clutch (15); the other end of the clutch (15) is respectively connected to the other end of the first ball valve (13) and one end of the second ball valve (14); the other end of the second ball valve (14) is connected to the third input end of the electro-hydraulic proportional valve (12); and the second output end of the pressure regulating valve (11) is connected to the lubricating oil tank.

3. A hydraulic control system for a clutch as claimed in claim 1, characterized in that: A cooler (6) and a filter (7) are arranged in sequence between the first lubricating oil pump (1) and the pressure regulating valve (11).

4. A hydraulic control system for a clutch as claimed in claim 3, characterized in that: A one-way valve (3) and a throttle valve (5) are provided between the first lubricating oil pump (1) and the cooler (6).

5. A hydraulic control system for a clutch as claimed in claim 3, characterized in that: A safety valve (4) is also provided directly between the throttle valve (5) and the lubricating oil tank.

6. A hydraulic control system for a clutch as claimed in claim 3, characterized in that: An oil filter (8) is also provided between the filter 7 and the first electromagnetic control valve 9.

7. A hydraulic control system for a clutch as claimed in claim 2, characterized in that: A first pressure sensor, a temperature sensor, an overflow valve, a lubricating bearing, and a lubricating gear are also arranged between the pressure regulating valve (11) and the clutch (15).

8. A hydraulic control method for a clutch, characterized in that: The control method is used for the control system according to any one of claims 1 to 7, and specifically includes a first control method: First, the first ball valve (13) is opened, and the second ball valve (14), the third ball valve (16), and the electro-hydraulic proportional valve (12) are closed at the same time; Then, the first lubricating oil pump (1) is started, and the lubricating oil from the lubricating oil tank passes through the first lubricating oil pump (1) and reaches the pressure regulating valve (11). At this time, the first electromagnetic control valve (9) and the second electromagnetic control valve (10) perform the first interlocking control action, and the pressure gradually increases to reach the stable torque transmission stage of the clutch, completing the entire process of the clutch soft shifting.

9. A hydraulic control method for a clutch as claimed in claim 8, characterized in that: Also includes a second control method: First, the second ball valve (14), the third ball valve (16), and the electro-hydraulic proportional valve (12) are opened, and the first ball valve (13) is closed at the same time; Then, the first lubricating oil pump (1) is started, and the lubricating oil from the lubricating oil tank passes through the first lubricating oil pump (1) and reaches the pressure regulating valve (11). At this time, the first electromagnetic control valve (9) and the electro-hydraulic proportional valve (12) perform the second interlocking control action, and the oil pressure rises linearly from 0 until the clutch reaches stable torque transmission, completing the soft clutch shifting.

10. A hydraulic control method for a clutch as claimed in claim 8, characterized in that: Also includes a third control method: First, the first ball valve (13) and the electro-hydraulic proportional valve (12) are opened, and the second ball valve (14) and the third ball valve (16) are closed at the same time; Then, the first lubricating oil pump (1) is started, and the lubricating oil from the lubricating oil tank passes through the first lubricating oil pump (1) and reaches the pressure regulating valve (11). At this time, the first electromagnetic control valve (9) and the electro-hydraulic proportional valve (12) perform the third interlocking control action, and the oil pressure rises linearly until the clutch reaches stable torque transmission, completing the soft clutch shifting.

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