Hydraulic control system for power-shift transmission and power-shift transmission

Abstract

The application discloses a hydraulic control system for a power shift transmission, comprising a main control module A, a gear control module B, a gear execution module C and a diagnosis module D; the main control module A comprises a main oil circuit, a back oil circuit, a lubricating oil circuit, a torque converter inlet oil circuit and a torque converter outlet oil circuit; the hydraulic control system realizes oil filling control of different clutch pistons through control of electromagnetic valves, and further realizes gear control of the transmission; the hydraulic control system has a total of eight forward gears and four reverse gears, can realize pressure interlocking between a 1st-gear clutch oil circuit and a 3rd-gear clutch oil circuit, and pressure interlocking between a 2nd-gear clutch oil circuit and a 4th-gear clutch oil circuit; can realize pressure interlocking between a forward-gear clutch inlet oil circuit and a reverse-gear clutch control oil circuit, and can realize interlocking functions of multiple gears. The hydraulic control system also has a self-diagnosis function, and can realize real-time monitoring of electrical elements in the hydraulic control system.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of transmission, and relates to a hydraulic control system for a power shift transmission and the power shift transmission. BACKGROUND

[0002] The engine and the transmission are key components of engineering machinery, road vehicles and special equipment. With the continuous progress of science and technology, the electro-hydraulic control system automatic transmission with good controllability and safety can effectively improve and improve the quality and use efficiency of the machinery, lay a foundation for subsequent remote control, and has become a necessary choice in the intelligent process of engineering machinery and special equipment fields.

[0003] At present, the main engineering machinery manufacturers mainly use imported transmission products. The design of the products is old, the hydraulic system can only realize the basic function, and defects exist in safety, reliability and hydraulic system diagnosis. The various valves used in the hydraulic control system of the transmission belong to consumable parts. When the hydraulic control system fails, the related maintenance personnel need to measure each monitoring point in the fault hydraulic system in real time to find the fault, which causes a long maintenance period and high maintenance cost.

[0004] As described above, since the demand for the transmission for engineering machinery is developing towards high controllability, high reliability, high safety and intelligentization capable of realizing self-diagnosis, the power shift transmission with the safety locking function and the self-diagnosis function has good development potential, but the existing technology does not have a hydraulic control system integrating the safety locking function and the self-diagnosis function. SUMMARY

[0005] In view of the defects and deficiencies in the prior art, the application provides a hydraulic control system for a power shift transmission and the power shift transmission, to solve the technical problem that the prior art lacks a hydraulic control system for a power shift transmission with a safety locking function and a hydraulic control module fault point self-diagnosis function.

[0006] To achieve the above purpose, the application adopts the following technical scheme:

[0007] A hydraulic control system for a power shift transmission, comprising a main control module A, a gear control module B, a gear execution module C and a diagnosis module D; the main control module A comprises a main oil circuit a and a return oil circuit c;

[0008] The gear control module B comprises a first switch valve, a first proportional pressure regulating valve, a second switch valve, a hydraulic control reversing valve, a second proportional pressure regulating valve, a third proportional pressure regulating valve, a fourth proportional pressure regulating valve, a fifth proportional pressure regulating valve, a third switch valve, a sixth proportional pressure regulating valve, a fourth switch valve, a hydraulic control proportional valve and a gear pressure supply oil circuit g;

[0009] The gear execution module C comprises a hydraulic torque converter;

[0010] The diagnostic module D comprises a hydraulic control proportional valve;

[0011] The first proportional pressure regulating valve inlet, the second switch valve inlet, the hydraulic control reversing valve inlet, the fourth proportional pressure regulating valve inlet, the fifth proportional pressure regulating valve inlet and the sixth proportional pressure regulating valve inlet are connected to the gear pressure supply oil path g.

[0012] The first switch valve inlet is connected to the main oil path a, and the first switch valve has two outlets, one of which is connected to the oil return path c, and the other is connected to the hydraulic control proportional valve inlet and the gear pressure supply oil path g.

[0013] The first proportional pressure regulating valve outlet, the second switch valve outlet, the hydraulic control reversing valve outlet, the second proportional regulating valve outlet, the third proportional regulating valve outlet, the fourth proportional pressure regulating valve outlet, the fifth proportional pressure regulating valve outlet, the third switch valve outlet, the sixth proportional pressure regulating valve outlet and the fourth switch valve outlet are connected to the oil return path c.

[0014] The first proportional pressure regulating valve outlet is connected to the lock clutch cavity of the hydraulic torque converter.

[0015] The second switch valve outlet is connected to the hydraulic control reversing valve inlet.

[0016] The hydraulic control reversing valve outlet is connected to the second proportional regulating valve inlet and the third proportional regulating valve inlet.

[0017] The fifth proportional pressure regulating valve outlet is connected to the third switch valve inlet, and the sixth proportional pressure regulating valve outlet is connected to the fourth switch valve inlet.

[0018] The present application also has the following technical features:

[0019] Specifically, the first proportional pressure regulating valve outlet, the hydraulic control reversing valve outlet, the fourth proportional pressure regulating valve outlet, the fifth proportional pressure regulating valve outlet and the sixth proportional pressure regulating valve outlet are respectively provided with a first accumulator, a second accumulator, a third accumulator, a fourth accumulator and a fifth accumulator.

[0020] Further, the diagnostic module D further comprises a pressure sensor connected to the hydraulic control proportional valve.

[0021] Further, the main control module A further comprises an oil pool, a first oil pump, a second oil pump, a first pressure regulating valve, a third pressure regulating valve, a radiator, a torque converter inlet oil circuit b, a torque converter outlet oil circuit d and an oil suction oil circuit u, the oil suction oil circuit u is connected with the oil inlet of the first oil pump and the oil inlet of the second oil pump, and the oil suction oil circuit u is communicated with the oil pool;

[0022] The oil outlet of the first oil pump is connected with the main oil circuit a and the first pressure regulating valve respectively; the oil outlet of the first pressure regulating valve is connected with the torque converter inlet oil circuit b.

[0023] The oil outlet of the second oil pump is connected with the oil outlet of the radiator through a lubricating oil circuit f, the oil inlet of the radiator is connected with the oil outlet of the third pressure regulating valve, and the oil inlet of the third pressure regulating valve is connected with the torque converter outlet oil circuit d.

[0024] Further, the main control module A further comprises a first filter, a second filter, a third filter, a first differential pressure switch, a second differential pressure switch, a third differential pressure switch, a first check valve and a second check valve.

[0025] The first filter is arranged on the oil inlet pipeline of the first oil pump and the second oil pump; the second filter is arranged on the oil outlet pipeline of the first oil pump, and the third filter is arranged on the oil outlet pipeline of the second oil pump; the first filter is connected with the first differential pressure switch in parallel, the second filter is connected with the second differential pressure switch in parallel, and the third filter is connected with the third differential pressure switch in parallel.

[0026] The first oil pump is connected with the first check valve in parallel, the oil inlet of the first check valve is communicated with the oil outlet of the first oil pump, and the oil outlet of the first check valve is communicated with the oil inlet of the first oil pump.

[0027] The second oil pump is connected with the second check valve in parallel, the oil inlet of the second check valve is communicated with the oil outlet of the second oil pump, and the oil outlet of the second check valve is communicated with the oil inlet of the second oil pump.

[0028] Further, the main control module A further comprises a second pressure regulating valve, the oil inlet of the second pressure regulating valve is connected with the torque converter inlet oil circuit b, and the oil outlet of the second pressure regulating valve is connected with the oil suction oil circuit u.

[0029] Further, the control port of the hydraulic control proportional valve is further connected with the oil outlet of the fifth proportional pressure regulating valve, the oil outlet of the sixth proportional pressure regulating valve, the oil outlet of the second switch valve and the oil outlet of the fourth proportional pressure regulating valve respectively; the control port of the hydraulic control reversing valve is connected with the oil outlet of the fourth proportional pressure regulating valve.

[0030] Further, the gear execution module C further comprises a first clutch piston, a second clutch piston, a third clutch piston, a fourth clutch piston, a fifth clutch piston, a sixth clutch piston and a seventh clutch piston.

[0031] The first clutch piston is connected with the oil outlet of the second proportional adjusting valve, the second clutch piston is connected with the oil outlet of the third proportional adjusting valve, the third clutch piston is connected with the oil outlet of the fourth proportional adjusting valve, the fourth clutch piston and the fifth clutch piston are respectively connected with the two oil outlets of the third switch valve, and the sixth clutch piston and the seventh clutch piston are respectively connected with the two oil outlets of the fourth switch valve.

[0032] Furthermore, a temperature sensor is arranged on the oil inlet pipeline of the first filter, and the temperature sensor is connected with the oil return pipeline c.

[0033] The application also protects a power shift transmission, wherein the power shift transmission is provided with the hydraulic control system for power shift transmission.

[0034] Compared with the prior art, the application has the following beneficial effects:

[0035] (1) The hydraulic control system of the application realizes the oil filling control of different clutch pistons through the control of each electromagnetic valve, thereby realizing the gear control of the transmission, the hydraulic control system disclosed by the application has 8 forward gears and 4 reverse gears, can realize the pressure interlocking between the 1st clutch oil circuit and the 3rd clutch oil circuit and the pressure interlocking between the 2nd clutch oil circuit and the 4th clutch oil circuit, can realize the pressure interlocking between the forward clutch inlet oil circuit and the reverse clutch control oil circuit, and can realize the interlocking function of multiple gears.

[0036] (2) The hydraulic control system of the application is provided with the first switch valve, so that the transmission can directly retreat to the neutral gear and ensure that no clutch is combined during the neutral gear, in the actual use of the transmission, the clutch of the non-required gear can be avoided to be combined, the internal freedom degree is prevented from being confused, the internal parts of the transmission are prevented from being damaged, and the application of the hydraulic system is safer.

[0037] (3) The hydraulic control system of the application is provided with the diagnosis module containing the hydraulic control proportional valve and the pressure sensor, so that the hydraulic control system has the self-diagnosis function, the diagnosis module can realize the real-time monitoring of each electrical element in the hydraulic control system, does not need the intervention of the relevant professional personnel for detection, can directly locate the fault point when the electrical element of the hydraulic control system fails, shortens the repair cycle, and reduces the maintenance cost. BRIEF DESCRIPTION OF DRAWINGS

[0038] Fig. 1 is the hydraulic principle diagram of the hydraulic control system of the application;

[0039] Fig. 2 is the hydraulic principle diagram of the labeling module of the application;

[0040] Fig. 3The hydraulic schematic diagram of the present application is annotated with oil circuit annotations.

[0041] The meaning of the reference signs is as follows:

[0042] A - main control module, B - gear control module, C - execution module, D - diagnosis module;

[0043] 1 - oil tank, 2 - temperature sensor, 3 - first filter, 4 - first differential pressure switch, 5 - first oil pump, 6 - first check valve, 7 - second filter, 8 - second differential pressure switch, 9 - second oil pump, 10 - second check valve, 11 - third filter, 12 - third differential pressure switch, 13 - first pressure regulating valve, 14 - second pressure regulating valve, 15 - torque converter, 16 - third pressure regulating valve, 17 - radiator, 18 - first on-off valve, 19 - first proportional pressure regulating valve, 20 - first accumulator, 21 - second on-off valve, 22 - hydraulic directional control valve, 23 - second accumulator, 24 - second proportional pressure regulating valve, 25 - first clutch piston, 26 - third proportional pressure regulating valve, 27 - second clutch piston, 28 - fourth proportional pressure regulating valve, 29 - third accumulator, 30 - third clutch piston, 31 - fifth proportional pressure regulating valve, 32 - fourth accumulator, 33 - third on-off valve, 34 - fourth clutch piston, 35 - fifth clutch piston, 36 - sixth proportional pressure regulating valve, 37 - fifth accumulator, 38 - fourth on-off valve, 39 - sixth clutch piston, 40 - seventh clutch piston, 41 - hydraulic proportional valve, 42 - pressure sensor;

[0044] a - main oil circuit, b - torque converter inlet oil circuit, c - return oil circuit, d - torque converter outlet oil circuit, e - cooler inlet oil circuit, f - lubricating oil circuit, g - gear pressure supply oil circuit, h - torque converter lock-up clutch oil circuit, i - forward gear clutch lock-up valve inlet oil circuit, j - forward gear clutch inlet oil circuit, k - low speed forward gear clutch control oil circuit, l - high speed forward gear clutch oil circuit, m - reverse gear clutch control oil circuit, n - 1 / 3 gear clutch control oil circuit, o - 1 gear clutch oil circuit, p - 3 gear clutch oil circuit, q - 2 / 4 gear clutch control oil circuit, r - 2 gear clutch oil circuit, s - 4 gear clutch oil circuit, t - diagnosis pressure measurement oil circuit, u - oil suction oil circuit.

[0045] The present application will be described in detail below in conjunction with the accompanying drawings and specific embodiments. DETAILED DESCRIPTION

[0046] In accordance with the above technical solutions, the following specific embodiments of the present application are given, and it should be noted that the present application is not limited to the following specific embodiments, and any equivalent variations made on the basis of the technical solutions of the present application shall fall within the protection scope of the present application. The present application is further described in detail below in combination with the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative labor shall fall within the protection scope of the present application.

[0047] It should be noted that the terms "comprising" and "having" and any variations thereof in the present application are intended to cover non-exclusive inclusion, for example, a process, method, system, product or device comprising a series of steps or units need not be limited to only those steps or units clearly listed, but can include other steps or units not clearly listed or inherent to these processes, methods, products or devices.

[0048] Embodiment 1

[0049] In accordance with the above technical solutions, as shown in Figs. 1 to 3 the present embodiment provides a hydraulic control system for a power shift transmission, which comprises a main control module A, a gear control module B, a gear execution module C and a diagnosis module D; the main control module A is used to provide a hydraulic source for realizing functions of each element of the transmission; the gear control module B is a set of logical control elements for realizing gear shifting, and is used to provide a logical control signal for gear shifting; the gear execution module C is a set of execution elements for gear shifting, and is used to realize power shift of the transmission; and the diagnosis module D is used for fault diagnosis of the hydraulic control system.

[0050] The main control module A comprises an oil pool 1, a temperature sensor 2, a first filter 3, a first differential pressure switch 4, a first oil pump 5, a first check valve 6, a second filter 7, a second differential pressure switch 8, a second oil pump 9, a second check valve 10, a third filter 11, a third differential pressure switch 12, a first pressure regulating valve 13, a second pressure regulating valve 14, a third pressure regulating valve 16, a radiator 17, and a main oil circuit a, a torque converter inlet oil circuit b, a return oil circuit c, a torque converter outlet oil circuit d, a cooler inlet oil circuit e, a lubricating oil circuit f and an oil suction circuit u.

[0051] The oil pool 1 is used to store hydraulic oil, the temperature sensor 2 is used to measure the temperature of the hydraulic oil, the first filter 3, the second filter 7 and the third filter 11 are used to filter the hydraulic oil, the first differential pressure switch 4, the second differential pressure switch 8 and the third differential pressure switch 12 are connected when a certain pressure difference appears between the two sides of the oil circuit, so as to ensure that the hydraulic system can work normally when the corresponding filter is blocked. The first pressure regulating valve 13, the second pressure regulating valve 14 and the third pressure regulating valve 16 are all used for pressure regulation of the corresponding oil circuit; and the radiator 17 is used to reduce the temperature of the hydraulic oil.

[0052] Wherein, the main control module A and the gear control module B are communicated through the main oil path a and the return oil path c, and the execution module C is connected with the main control module A and the gear control module B. The main oil path a is an output oil path of the main control module A, and is also a pressure source of the gear control module B.

[0053] The gear control module B comprises a first switch valve 18, a first proportional pressure regulating valve 19, a second switch valve 21, a hydraulic control reversing valve 22, a second proportional pressure regulating valve 24, a third proportional pressure regulating valve 26, a fourth proportional pressure regulating valve 28, a fifth proportional pressure regulating valve 31, a third switch valve 33, a sixth proportional pressure regulating valve 36, a fourth switch valve 38, a hydraulic control proportional valve 41 and a gear pressure supply oil path g; further comprising a torque converter lock-up clutch oil path h, a forward gear clutch lock-up valve oil inlet oil path i, a forward gear clutch oil inlet oil path j, a low-speed forward gear clutch control oil path k, a high-speed forward gear clutch control oil path l, a reverse gear clutch control oil path m, a 1 / 3 gear clutch control oil path n, a 1 gear clutch oil path o, a 3 gear clutch oil path p, a 2 / 4 gear clutch control oil path q, a 2 gear clutch oil path r, a 4 gear clutch oil path s and a diagnostic pressure measurement oil path t.

[0054] Wherein, the first switch valve 18 is a neutral control valve, and the second switch valve 21 is a forward gear clutch control valve; the third switch valve 33 and the fourth switch valve 38 are clutch pressure selection valves; the first proportional pressure regulating valve 19, the second proportional pressure regulating valve 24, the third proportional pressure regulating valve 26, the fourth proportional pressure regulating valve 28, the fifth proportional pressure regulating valve 31 and the sixth proportional pressure regulating valve 36 are used for pressure regulation of the clutch; the hydraulic control reversing valve 22 is used for locking of the clutch, and the hydraulic control proportional valve 41 is used for pressure control of the hydraulic system for diagnosis.

[0055] In the embodiment, the first switch valve 18 and the second switch valve 21 are both two-position three-way electromagnetic switch valves, the third switch valve 33 and the fourth switch valve 38 are both two-position four-way electromagnetic switch valves, the first proportional pressure regulating valve 19, the second proportional pressure regulating valve 24, the third proportional pressure regulating valve 26, the fourth proportional pressure regulating valve 28, the fifth proportional pressure regulating valve 31 and the sixth proportional pressure regulating valve 36 are all two-position three-way electromagnetic proportional pressure regulating valves, and the hydraulic control reversing valve 22 is a two-position three-way hydraulic control reversing valve; the hydraulic control proportional valve 41 is a two-position three-way hydraulic control proportional valve.

[0056] Specifically, the first switch valve 18 is connected with the main oil path a at the inlet and the gear pressure supply oil path g at the outlet. The first switch valve 18 can make the transmission directly retreat to the neutral gear, and ensure that the clutch is not combined during the neutral gear, so that the application of the hydraulic system is safer. The third switch valve 33 can realize the interlocking of the 1st clutch oil path o and the 3rd clutch oil path p, so as to ensure that the hydraulic system will not appear the 1st and 3rd clutch pressure confusion. The fourth switch valve 38 can realize the interlocking of the 2nd clutch oil path r and the 4th clutch oil path s, so as to ensure that the hydraulic system will not appear the 2nd and 4th clutch pressure confusion.

[0057] The gear execution module C includes a hydraulic torque converter 15, which is a three-channel hydraulic transmission device for transmitting speed and torque.

[0058] The diagnosis module D includes a hydraulic control proportional valve 41 and a pressure sensor 42 connected and arranged.

[0059] The hydraulic control proportional valve 41 is affected by the pressure of the forward clutch lock valve inlet oil path i, the reverse clutch control oil path m, the 1st / 3rd clutch control oil path n and the 2nd / 4th clutch control oil path q. The pressure sensor 42 will read different pressure values according to the different states of the control end, so that the detection does not need the intervention of relevant professionals. When the electrical elements of the hydraulic control system fail, the fault point can be directly located, the maintenance cycle is shortened, and the maintenance cost is reduced.

[0060] The inlet of the first proportional pressure regulating valve 19, the inlet of the second switch valve 21, the inlet of the fourth proportional pressure regulating valve 28, the inlet of the fifth proportional pressure regulating valve 31, the inlet of the sixth proportional pressure regulating valve 36 and the inlet of the hydraulic control proportional valve 41 are all connected with the gear pressure supply oil path g.

[0061] The drain of the first proportional pressure regulating valve 19, the drain of the second switch valve 21, the drain of the hydraulic control reversing valve 22, the drain of the second proportional regulating valve 24, the drain of the third proportional regulating valve 26, the drain of the fourth proportional pressure regulating valve 28, the drain of the fifth proportional pressure regulating valve 31, the drain of the third switch valve 33, the drain of the sixth proportional pressure regulating valve 36 and the drain of the fourth switch valve 38 are all connected with the oil return oil path c, and then connected to the oil pool 1.

[0062] The outlet of the first proportional pressure regulating valve 19 is connected with the torque converter lock clutch oil path h, which is connected with the lock clutch cavity of the hydraulic torque converter 15 and the first accumulator 20 for lock clutch pressure stabilization in two ways.

[0063] The outlet of the second switch valve 21 is connected with the forward clutch lock valve inlet oil path i, which is connected with the control end of the hydraulic control proportional valve 41 and the inlet of the hydraulic control reversing valve 22.

[0064] One control end of the hydraulic control reversing valve 22 is connected with the pressure supply oil path g, the other control end is connected with the reverse gear clutch control oil path m, the oil outlet of the hydraulic control reversing valve 22 is connected with the forward gear clutch inlet oil path i, which is connected with the oil inlet of the second proportional regulating valve 24 and the oil inlet of the third proportional regulating valve 26 respectively; the hydraulic control reversing valve 22 can realize the locking of the forward gear clutch inlet oil path i and the reverse gear clutch control oil path m, so as to ensure that the hydraulic system will not appear the forward and reverse clutch pressure confusion.

[0065] The oil outlet of the fifth proportional pressure regulating valve 31 is connected with the oil inlet of the third on-off valve 33, and the oil outlet of the sixth proportional pressure regulating valve 36 is connected with the oil inlet of the fourth on-off valve 38.

[0066] As a preferred scheme of the embodiment, the oil outlet of the hydraulic control reversing valve 22, the oil outlet of the fourth proportional pressure regulating valve 28, the oil outlet of the fifth proportional pressure regulating valve 31 and the oil outlet of the sixth proportional pressure regulating valve 36 are respectively provided with the second accumulator 23, the third accumulator 29, the fourth accumulator 32 and the fifth accumulator 37.

[0067] The second accumulator 23 is used to stabilize the pressure to the first clutch piston 25 and the second clutch piston 27, so as to improve the control effect of the clutch; the third accumulator 29 is used to stabilize the pressure to the third clutch piston 30, so as to improve the control effect of the clutch; the fourth accumulator 32 is used to stabilize the pressure to the fourth clutch piston 34 and the fifth clutch piston 35, so as to improve the control effect of the clutch; the fifth accumulator 37 is used to stabilize the pressure to the sixth clutch piston 39 and the seventh clutch piston 40, so as to improve the control effect of the clutch.

[0068] Specifically, the oil outlet of the fourth proportional pressure regulating valve 28 is connected with the reverse gear clutch control oil path m, and the reverse gear clutch control oil path m is connected with the locking clutch cavity of the third accumulator 29 and the third clutch piston 30.

[0069] The oil outlet of the fifth proportional pressure regulating valve 31 is connected with the 1 / 3 gear clutch control oil path n, and the 1 / 3 gear clutch control oil path n is connected with the locking clutch cavity of the fourth accumulator 32 and the oil inlet of the third on-off valve 33, and the oil path is also connected with the control end of the hydraulic proportional valve 41.

[0070] The oil outlet of the sixth proportional pressure regulating valve 36 is connected with the 2 / 4 gear clutch control oil path q, and the oil path is connected with the locking clutch cavity of the fifth accumulator 37 and the oil inlet of the fourth on-off valve 38, and the oil path is also connected with the control end of the hydraulic proportional valve 41.

[0071] As a preferred scheme of the embodiment, the hydraulic proportional valve 41 is also connected with the pressure sensor 42.

[0072] As a preferred scheme of the embodiment, the oil inlet of the first oil pump 5 and the oil inlet of the second oil pump 9 are connected with the oil suction line u, and the oil suction line u is communicated with the oil pool 1; the first oil pump 5 provides a hydraulic source for the entire hydraulic control system, and the second oil pump 9 provides a hydraulic source for supplementing oil in the lubricating oil line f.

[0073] The oil outlet of the first oil pump 5 is connected with the main oil line a and the first pressure regulating valve 13 respectively; the oil outlet of the first pressure regulating valve 13 is connected with the torque converter inlet oil line b.

[0074] The oil outlet of the second oil pump 9 is connected with the radiator 17 through the lubricating oil line f, the oil inlet of the radiator 17 is connected with the oil outlet of the third pressure regulating valve 16, and the oil inlet of the third pressure regulating valve 16 is connected with the torque converter outlet oil line d.

[0075] The first pressure regulating valve 13, the second pressure regulating valve 14 and the third pressure regulating valve 16 can adjust the pressure of the oil inlets thereof respectively, and are used for regulating the system main oil pressure, the torque converter inlet oil pressure and the torque converter outlet oil pressure respectively. The radiator 17 is used for radiating the oil to ensure that the temperature of the oil does not exceed the use requirement.

[0076] As a preferred scheme of the embodiment, the first filter 3 is arranged on the oil inlet pipeline of the first oil pump 5 and the second oil pump 9; the second filter 7 is arranged on the oil outlet pipeline of the first oil pump 5, and the third filter 11 is arranged on the oil outlet pipeline of the second oil pump 9; the first filter 3 is connected with the first pressure difference switch 4 in parallel, the second filter 7 is connected with the second pressure difference switch 8 in parallel, and the third filter 11 is connected with the third pressure difference switch 12 in parallel. The first filter 3 is a pre-filter of the first oil pump 5 and the second oil pump 9, so that relatively clean oil is sucked into the first oil pump 5 and the second oil pump 9; the second filter 7 is a post-filter of the first oil pump 5, so as to ensure the cleanliness of the oil entering the valves in the system; and the third filter 11 is a post-filter of the second oil pump 9, so as to ensure the cleanliness of the oil entering the lubricating oil line f. The oil outlet of the second filter 7 is divided into two lines, one of which is communicated with the oil inlet of the first pressure regulating valve 13 on the main oil line a, and the other of which is communicated with the gear control module B.

[0077] The first oil pump 5 is connected with the first one-way valve 6 in parallel, the oil inlet of the first one-way valve 6 is communicated with the oil outlet of the first oil pump 5, and the oil outlet of the first one-way valve 6 is communicated with the oil inlet of the first oil pump 5.

[0078] The second oil pump 9 is connected with the second one-way valve 10 in parallel, the oil inlet of the second one-way valve 10 is communicated with the oil outlet of the second oil pump 9, and the oil outlet of the second one-way valve 10 is communicated with the oil inlet of the second oil pump 9.

[0079] Specifically, the oil suction port of the first oil pump 5, the oil discharge port of the first one-way valve 6, the oil suction port of the second oil pump 9 and the oil discharge port of the second one-way valve 10 are connected with the oil suction line u, and the oil suction line u is communicated with the oil pool 1.

[0080] As a preferred solution of the embodiment, the second pressure regulating valve 14 is connected to the torque converter inlet oil passage b at its inlet, and to the oil return passage c at its outlet.

[0081] As a preferred solution of the embodiment, the control ports of the hydraulic control proportional valve 41 are respectively connected to the outlet of the fifth proportional pressure regulating valve 31, the outlet of the sixth proportional pressure regulating valve 36, the outlet of the second switch valve 21 and the outlet of the fourth proportional pressure regulating valve 28; the control port of the hydraulic control reversing valve is connected to the outlet of the fourth proportional pressure regulating valve 28.

[0082] As a preferred solution of the embodiment, the gear execution module C further comprises a first clutch piston 25, a second clutch piston 27, a third clutch piston 30, a fourth clutch piston 34, a fifth clutch piston 35, a sixth clutch piston 39 and a seventh clutch piston 40.

[0083] The first clutch piston 25 is connected to the outlet of the second proportional regulating valve 24 through the low-speed forward gear clutch control oil passage k, the second clutch piston 27 is connected to the outlet of the third proportional regulating valve 26 through the high-speed forward gear clutch control oil passage l, the third clutch piston 30 is connected to the outlet of the fourth proportional regulating valve 28 through the reverse gear clutch control oil passage m, the fourth clutch piston 34 is connected to one outlet of the third switch valve 33 through the 1-gear clutch oil passage o, the fifth clutch piston 35 is connected to one outlet of the third switch valve 33 through the 3-gear clutch oil passage p, the sixth clutch piston 39 is connected to one outlet of the fourth switch valve 38 through the 2-gear clutch oil passage r, and the seventh clutch piston 40 is connected to one outlet of the fourth switch valve 38 through the 4-gear clutch oil passage s.

[0084] The lock-up clutch of the torque converter 15 is controlled by the first proportional pressure regulating valve 19; the first clutch piston 25 is a low-speed forward gear clutch piston controlled by the second proportional pressure regulating valve 24; the second clutch piston 27 is a high-speed forward gear clutch piston controlled by the third proportional pressure regulating valve 26; the hydraulic source of the second proportional pressure regulating valve 24 and the third proportional pressure regulating valve 26 is controlled by the second switch valve 21 and the hydraulic control reversing valve 22; the third clutch piston 30 is a reverse gear clutch piston controlled by the fourth proportional pressure regulating valve 28; the fourth clutch piston 34 is a 1-gear clutch piston, the fifth clutch piston 35 is a 3-gear clutch piston, and the fourth clutch piston 34 and the fifth clutch piston 35 are controlled by the fifth proportional pressure regulating valve 31 and the third switch valve; the sixth clutch piston 39 is a 2-gear clutch piston, and the seventh clutch piston 40 is a 4-gear clutch piston, and the sixth clutch piston 39 and the seventh clutch piston 40 are controlled by the sixth proportional pressure regulating valve 36 and the fourth switch valve 38.

[0085] As a preferred scheme of the embodiment, the temperature sensor 2 is arranged on the oil inlet pipeline of the first filter 3, and the temperature sensor 2 is connected to the oil return pipeline c.

[0086] The working principle of the embodiment is as follows:

[0087] When a certain pressure difference appears in the oil pipelines on both sides of the first differential pressure switch 4, the second differential pressure switch 8 and the third differential pressure switch 12, the oil pipelines on both sides of the differential pressure switch are connected, so that the filter can work normally when it is blocked, and an alarm signal is provided.

[0088] In the unpowered state, the first switch valve 18 connects the gear pressure supply pipeline g and the oil return pipeline c, and blocks the main oil pipeline a. In the powered state, the first switch valve 18 connects the gear pressure supply pipeline g and the main oil pipeline a, and blocks the oil return pipeline c. The first switch valve 18 directly controls the valve inlet oil pressure related to other clutch controls, can quickly return to neutral, and realizes a safer gear control function.

[0089] In the unpowered state, the first proportional pressure regulating valve 19 connects the torque converter lock-up clutch oil pipeline h and the oil return pipeline c, and blocks the gear pressure supply pipeline g. In the powered state, the first proportional pressure regulating valve 19 connects the torque converter lock-up clutch oil pipeline h and the gear pressure supply pipeline g, and blocks the oil return pipeline c. The valve is a proportional valve, which can regulate the pressure of the torque converter lock-up clutch oil pipeline h leading to the torque converter lock-up clutch.

[0090] In the unpowered state, the fourth proportional pressure regulating valve 28 connects the reverse gear clutch control oil pipeline m and the oil return pipeline c, and blocks the gear pressure supply pipeline g. In the powered state, the fourth proportional pressure regulating valve 28 connects the reverse gear clutch control oil pipeline m and the gear pressure supply pipeline g, and blocks the oil return pipeline c. The valve is a proportional valve, which can regulate the pressure of the reverse gear clutch control oil pipeline m leading to the third clutch piston 30.

[0091] In the unpowered state, the fifth proportional pressure regulating valve 31 connects the 1 / 3 gear clutch control oil pipeline n and the oil return pipeline c, and blocks the gear pressure supply pipeline g. In the powered state, the fifth proportional pressure regulating valve 31 connects the 1 / 3 gear clutch control oil pipeline n and the gear pressure supply pipeline g, and blocks the oil return pipeline c. The valve is a proportional valve, which can regulate the pressure of the 1 / 3 gear clutch control oil pipeline n leading to the third switch valve 33.

[0092] The third switch valve 33, in the state of no electricity, connects the 1 / 3 clutch control oil way n and the 3 clutch oil way p, and connects the 1 clutch oil way o and the return oil way c; in the state of electricity, connects the 1 / 3 clutch control oil way n and the 1 clutch oil way o, and connects the 3 clutch oil way p and the return oil way c. The valve realizes the selection function of the 1 / 3 clutch control oil way n and the 1 clutch oil way o to the fourth clutch piston 34 and the 3 clutch oil way p to the fifth clutch piston 35.

[0093] The sixth proportional pressure regulating valve 36, in the state of no electricity, connects the 2 / 4 clutch control oil way q and the return oil way c, and blocks the gear pressure supply oil way g; in the state of electricity, connects the 2 / 4 clutch control oil way q and the gear pressure supply oil way g, and blocks the return oil way c. The valve is a proportional valve, which can adjust the pressure of the 2 / 4 clutch control oil way q to the fourth switch valve 38.

[0094] The fourth switch valve 38, in the state of no electricity, connects the 2 / 4 clutch control oil way q and the 4 clutch oil way s, and connects the 2 clutch oil way r and the return oil way c; in the state of electricity, connects the 2 / 4 clutch control oil way q and the 2 clutch oil way r, and connects the 4 clutch oil way s and the return oil way c. The valve realizes the selection function of the 2 / 4 clutch control oil way q and the 2 clutch oil way r to the sixth clutch piston 39 and the 4 clutch oil way s to the seventh clutch piston 40.

[0095] The second switch valve 21, in the state of no electricity, connects the forward clutch lock valve inlet oil way i and the return oil way c, and blocks the gear pressure supply oil way g; in the state of electricity, connects the forward clutch lock valve inlet oil way i and the gear pressure supply oil way g, and blocks the return oil way c. The valve realizes the overall control of the forward clutch oil supply.

[0096] The hydraulic control reversing valve 22, when only subjected to the pressure of the gear pressure supply oil way g, connects the forward clutch inlet oil way j and the forward clutch lock valve inlet oil way i, and blocks the return oil way c; when subjected to the pressure of the gear pressure supply oil way g and the reverse clutch control oil way m at the same time, connects the forward clutch inlet oil way j and the return oil way c, and blocks the forward clutch lock valve inlet oil way i. The setting of the valve can ensure that the forward clutch inlet oil way j or the reverse clutch control oil way exists pressure, that is, it ensures that the forward gear and the reverse gear cannot exist oil pressure at the same time.

[0097] The second proportional pressure regulating valve 24 is in communication with the low-speed forward clutch control oil passage k and the oil return passage c in the non-energized state, and the forward clutch inlet oil passage j is blocked; in the energized state, the low-speed forward clutch control oil passage k and the forward clutch inlet oil passage j are in communication, and the oil return passage c is blocked. The valve is a proportional valve, which can regulate the pressure of the low-speed forward clutch control oil passage k leading to the first clutch piston 25.

[0098] The third proportional pressure regulating valve 26 is in communication with the high-speed forward clutch control oil passage l and the oil return passage c in the non-energized state, and the forward clutch inlet oil passage j is blocked; in the energized state, the high-speed forward clutch control oil passage l and the forward clutch inlet oil passage j are in communication, and the oil return passage c is blocked. The valve is a proportional valve, which can regulate the pressure of the high-speed forward clutch control oil passage l leading to the second clutch piston 27.

[0099] The hydraulic control proportional valve 41 in the hydraulic control system is affected by the forward clutch lock valve inlet oil passage i, the reverse clutch control oil passage m, the 1 / 3 clutch control oil passage n, and the 2 / 4 clutch control oil passage q; in the free state, the diagnostic pressure measuring oil passage t is in communication with the gear pressure supply oil passage g, and the oil return passage c is blocked; when affected by the control oil passage pressure, the diagnostic pressure measuring oil passage t is in communication with the oil return passage c, and the gear pressure supply oil passage g is blocked. When affected by different control oil passage pressures, the valve adjusts the pressure of the diagnostic pressure measuring oil passage t to different values.

[0100] The pressure sensor 42 is in communication with the diagnostic pressure measuring oil passage t, which is used to monitor the pressure in the regulated state of the hydraulic control proportional valve in real time, and provides information for system diagnosis.

[0101] The first accumulator 20, the second accumulator 23, the third accumulator 29, the fourth accumulator 32, and the fifth accumulator 37 stabilize the pressures of the torque converter lock-up clutch oil passage h, the forward clutch inlet oil passage j, the reverse clutch control oil passage m, the 1 / 3 clutch control oil passage n, and the 2 / 4 clutch control oil passage q, respectively.

[0102] The self-diagnosis method is as follows:

[0103] The pressure sensor 42 can read 17 kinds of pressures, P0-P16, among which P0, P4, P6, P7, P8, and P9 are pressure values in the normal gear state. When the gear speed ratio and the corresponding diagnostic pressure are correct, it can be determined that each element is working normally. When the speed ratio is abnormal, the diagnostic pressure value can be used to find the fault. The specific hydraulic control system diagnosis information is shown in Table 2.

[0104]

[0105] Table 1. Hydraulic control system diagnosis logic

[0106] Specific self-diagnosis pressure information includes:

[0107] First switch valve 18 is not powered: hydraulic control proportional valve 41 has no pressure source, and the pressure of the diagnostic pressure measuring oil path t is finally connected back to the oil return oil path c, and the pressure value is P0;

[0108] First switch valve 18 is powered: when the hydraulic control proportional valve 41 is not controlled by any pressure, the pressure of the diagnostic pressure measuring oil path t is the same as the pressure of the gear pressure supply oil path g, and the pressure value is P1;

[0109] When the hydraulic control proportional valve 41 is only controlled by the forward gear clutch lock valve inlet oil path i, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P2;

[0110] When the hydraulic control proportional valve 41 is only controlled by the reverse gear clutch control oil path m, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P3;

[0111] When the hydraulic control proportional valve 41 is only controlled by the 1 / 3 gear clutch control oil path n, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P4;

[0112] When the hydraulic control proportional valve 41 is only controlled by the 2 / 4 gear clutch control oil path q, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P5;

[0113] When the hydraulic control proportional valve 41 is controlled by the forward gear clutch lock valve inlet oil path i and the 1 / 3 gear clutch control oil path n, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P6;

[0114] When the hydraulic control proportional valve 41 is controlled by the forward gear clutch lock valve inlet oil path i and the 2 / 4 gear clutch control oil path q, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P7;

[0115] When the hydraulic control proportional valve 41 is controlled by the reverse gear clutch control oil path m and the 1 / 3 gear clutch control oil path n, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P8;

[0116] When the hydraulic control proportional valve 41 is controlled by the reverse gear clutch control oil path m and the 2 / 4 gear clutch control oil path q, the pressure of the diagnostic pressure measuring oil path t is adjusted by the hydraulic control proportional valve 41, and at this time the pressure value is P9;

[0117] When the hydraulic control proportional valve 41 is controlled by the forward clutch lock valve inlet oil path i and the reverse clutch control oil path m, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P10 at this time;

[0118] When the hydraulic control proportional valve 41 is controlled by the 1 / 3 clutch control oil path n and the 2 / 4 clutch control oil path q, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P11 at this time;

[0119] When the hydraulic control proportional valve 41 is controlled by the forward clutch lock valve inlet oil path i, the 1 / 3 clutch control oil path n and the 2 / 4 clutch control oil path q, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P12 at this time;

[0120] When the hydraulic control proportional valve 41 is controlled by the reverse clutch control oil path m, the 1 / 3 clutch control oil path n and the 2 / 4 clutch control oil path q, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P13 at this time;

[0121] When the hydraulic control proportional valve 41 is controlled by the forward clutch lock valve inlet oil path i, the reverse clutch control oil path m and the 1 / 3 clutch control oil path n, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P14 at this time;

[0122] When the hydraulic control proportional valve 41 is controlled by the forward clutch lock valve inlet oil path i, the reverse clutch control oil path m and the 2 / 4 clutch control oil path q, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P15 at this time;

[0123] When the hydraulic control proportional valve 41 is controlled by the forward clutch lock valve inlet oil path i, the reverse clutch control oil path m, the 1 / 3 clutch control oil path n and the 2 / 4 clutch control oil path q, the pressure of the diagnostic pressure measuring path t is regulated by the hydraulic control proportional valve 41, and the pressure value is P16 at this time.

[0124] The shifting method of the embodiment is as follows:

[0125] The hydraulic control system provided by the embodiment is applied in a power shifting automatic transmission, and three gear states are formed: neutral gear, forward gear and reverse gear.

[0126] Natural neutral gear: when the vehicle is in a starting state, i.e. a non-starting state, all the electromagnetic valves are not powered, which is a natural neutral gear state, i.e. all the electromagnetic valves are in a non-powered state; the pressure sensor 42 reads the pressure as P0, and if the read pressure is not P0.

[0127] Natural gear → preparatory gear: after the vehicle starts, there is a demand for use, control the first switch valve 18, the fifth proportional pressure regulating valve 31, the third switch valve 33, the fourth switch valve 38 power on, control the fourth clutch piston 34 to combine; The pressure sensor 42 reads the pressure as P4.

[0128] Preparatory gear → forward 1 gear: the second switch valve 21 is powered on, the second proportional pressure regulating valve 24 is powered on, and the first clutch piston 25 is controlled to be combined; The pressure sensor 42 reads the pressure as P6.

[0129] Forward 1 gear → forward 2 gear: the fifth proportional pressure regulating valve 31 is powered off, the sixth proportional pressure regulating valve 36 is powered on, the third switch valve 33 is powered off, and the sixth clutch piston 39 is controlled to be combined; The pressure sensor 42 reads the pressure as P7.

[0130] Forward 2 gear → forward 3 gear: the sixth proportional pressure regulating valve 36 is powered off, the fifth proportional pressure regulating valve 31 is powered on, the fourth switch valve 38 is powered off, and the fifth clutch piston 35 is controlled to be combined; The pressure sensor 42 reads the pressure as P6.

[0131] Forward 3 gear → forward 4 gear: the fifth proportional pressure regulating valve 31 is powered off, the sixth proportional pressure regulating valve 36 is powered on, the third switch valve 33 is powered on, and the seventh clutch piston 40 is controlled to be combined; The pressure sensor 42 reads the pressure as P7.

[0132] Forward 4 gear → forward 5 gear: the sixth proportional pressure regulating valve 36 is powered off, the second proportional pressure regulating valve 24 is powered off, the third proportional pressure regulating valve 26 is powered on, the fifth proportional pressure regulating valve 31 is powered on, and the fourth switch valve 38 is powered on. Control the second clutch piston 27 and the fourth clutch piston to combine; The pressure sensor 42 reads the pressure as P6.

[0133] Forward 5 gear → forward 6 gear: the fifth proportional pressure regulating valve 31 is powered off, the sixth proportional pressure regulating valve 36 is powered on, and the third switch valve 33 is powered off. Control the sixth clutch piston 39 to combine; The pressure sensor 42 reads the pressure as P7.

[0134] Forward 6 gear → forward 7 gear: the sixth proportional pressure regulating valve 36 is powered off, the fifth proportional pressure regulating valve 31 is powered on, and the fourth switch valve 38 is powered off. Control the fifth clutch piston 35 to combine; The pressure sensor 42 reads the pressure as P6.

[0135] Forward 7 gear → forward 8 gear: the fifth proportional pressure regulating valve 31 is powered off, the sixth proportional pressure regulating valve 36 is powered on, and the seventh clutch piston 40 is controlled to be combined; The pressure sensor 42 reads the pressure as P7.

[0136] Preparatory gear → reverse 1 gear: the fourth proportional pressure regulating valve 28 is powered on, and the third clutch piston 30 is controlled to be combined; The pressure sensor 42 reads the pressure as P8.

[0137] Reverse 1st gear → Reverse 2nd gear: The fifth proportional pressure regulating valve 31 is de-energized, the sixth proportional pressure regulating valve 36 is energized, the third switching valve 33 is de-energized, and the sixth clutch piston 39 is engaged; the pressure sensor 42 reads the pressure as P9.

[0138] Reverse 2 gear → Reverse 3 gear: The sixth proportional pressure regulating valve 36 is de-energized, the fifth proportional pressure regulating valve 31 is energized, the fourth switching valve 38 is de-energized, controlling the fifth clutch piston 35 to engage; the pressure sensor 42 reads the pressure as P8.

[0139] Reverse 3rd gear → Reverse 4th gear: The fifth proportional pressure regulating valve 31 is de-energized, the sixth proportional pressure regulating valve 36 is energized, the third switching valve 33 is energized, controlling the seventh clutch piston 40 to engage; the pressure sensor 42 reads the pressure as P9.

[0140] The shifting logic of the hydraulic control system is shown in Table 2:

[0141]

[0142] ☆: Solenoid valve is not energized; ★: Solenoid valve is energized; ◎: Solenoid valve can be energized or not.

[0143] Table 2. Shifting Logic of Hydraulic Control System

[0144] In addition, the hydraulic control system provided in this embodiment also has a self-diagnostic function, which can monitor each electrical component in the hydraulic control system in real time without the need for intervention by relevant professionals. When a fault occurs in the electrical component of the hydraulic control system, the fault point can be directly located, shortening the maintenance cycle and reducing maintenance costs.

[0145] Example 2

[0146] This embodiment provides a power shift transmission, which is equipped with the hydraulic control system for the power shift transmission provided in Embodiment 1.

[0147] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A hydraulic control system for a power-shift transmission, comprising a main control module A, a gear control module B, a gear execution module C, and a diagnosis module D, the main control module A comprising a main oil passage a and a return oil passage c, characterized in that, The gear control module B comprises a first switch valve (18), a first proportional pressure regulating valve (19), a second switch valve (21), a hydraulic control reversing valve (22), a second proportional pressure regulating valve (24), a third proportional pressure regulating valve (26), a fourth proportional pressure regulating valve (28), a fifth proportional pressure regulating valve (31), a third switch valve (33), a sixth proportional pressure regulating valve (36), a fourth switch valve (38), a hydraulic control proportional valve (41) and a gear pressure supply oil path g; The gear execution module C comprises a hydraulic torque converter (15); The diagnosis module D comprises a hydraulic control proportional valve (41); The first proportional pressure regulating valve (19) inlet, the second switch valve (21) inlet, the fourth proportional pressure regulating valve (28) inlet, the fifth proportional pressure regulating valve (31) inlet, the sixth proportional pressure regulating valve (36) inlet and the hydraulic control proportional valve (41) inlet are connected to the gear pressure supply oil path g; The first switch valve (18) inlet is connected to the main oil path a, and the outlet is connected to the gear pressure supply oil path g; The first proportional pressure regulating valve (19) outlet, the second switch valve (21) outlet, the hydraulic control reversing valve (22) outlet, the second proportional pressure regulating valve (24) outlet, the third proportional pressure regulating valve (26) outlet, the fourth proportional pressure regulating valve (28) outlet, the fifth proportional pressure regulating valve (31) outlet, the third switch valve (33) outlet, the sixth proportional pressure regulating valve (36) outlet and the fourth switch valve (38) outlet are connected to the return oil path c; The first proportional pressure regulating valve (19) outlet is connected to the lock clutch cavity of the hydraulic torque converter (15); The second switch valve (21) outlet is connected to the hydraulic control reversing valve (22) inlet; The hydraulic control reversing valve (22) outlet is connected to the second proportional pressure regulating valve (24) inlet and the third proportional pressure regulating valve (26) inlet respectively; The fifth proportional pressure regulating valve (31) outlet is connected to the third switch valve (33) inlet, and the sixth proportional pressure regulating valve (36) outlet is connected to the fourth switch valve (38) inlet; One control port of the hydraulic control reversing valve (22) is connected to the pressure supply oil path g; The control port of the hydraulic control proportional valve (41) is also connected to the fifth proportional pressure regulating valve (31) outlet, the sixth proportional pressure regulating valve (36) outlet, the second switch valve (21) outlet and the fourth proportional pressure regulating valve (28) outlet respectively; and the control port of the hydraulic control reversing valve (22) is connected to the fourth proportional pressure regulating valve (28) outlet; The gear execution module C further comprises a first clutch piston (25), a second clutch piston (27), a third clutch piston (30), a fourth clutch piston (34), a fifth clutch piston (35), a sixth clutch piston (39) and a seventh clutch piston (40). The first clutch piston (25) is connected with the oil outlet of the second proportional adjusting valve (24), the second clutch piston (27) is connected with the oil outlet of the third proportional adjusting valve (26), the third clutch piston (30) is connected with the oil outlet of the fourth proportional adjusting valve (28), the fourth clutch piston (34) and the fifth clutch piston (35) are respectively connected with the two oil outlets of the third switch valve (33), and the sixth clutch piston (39) and the seventh clutch piston (40) are respectively connected with the two oil outlets of the fourth switch valve (38).

2. The hydraulic control system for a powershift transmission as set forth in claim 1, wherein, The oil outlets of the first proportional pressure regulating valve (19), the hydraulic control reversing valve (22), the fourth proportional pressure regulating valve (28), the fifth proportional pressure regulating valve (31) and the sixth proportional pressure regulating valve (36) are respectively provided with the first accumulator (20), the second accumulator (23), the third accumulator (29), the fourth accumulator (32) and the fifth accumulator (37).

3. The hydraulic control system for a powershift transmission as set forth in claim 1, wherein, The diagnostic module D further comprises a pressure sensor (42) connected with the hydraulic control proportional valve (41).

4. The hydraulic control system for a powershift transmission of claim 1, wherein, The main control module A further comprises an oil pool (1), a first oil pump (5), a second oil pump (9), a first pressure regulating valve (13), a third pressure regulating valve (16), a radiator (17), a torque converter inlet oil path b, a torque converter outlet oil path d and an oil suction oil path u. The oil inlets of the first oil pump (5) and the second oil pump (9) are connected with the oil suction oil path u, and the oil suction oil path u is communicated with the oil pool (1). The oil outlets of the first oil pump (5) are respectively connected with the main oil path a and the first pressure regulating valve (13), and the oil outlet of the first pressure regulating valve (13) is connected with the torque converter inlet oil path b. The oil outlet of the second oil pump (9) is connected with the oil outlet of the radiator (17) through a lubricating oil path f, the oil inlet of the radiator (17) is connected with the oil outlet of the third pressure regulating valve (16), and the oil inlet of the third pressure regulating valve (16) is connected with the torque converter outlet oil path d.

5. The hydraulic control system for a powershift transmission as set forth in claim 4, wherein, The main control module A further comprises a first filter (3), a second filter (7), a third filter (11), a first differential pressure switch (4), a second differential pressure switch (8), a third differential pressure switch (12), a first check valve (6) and a second check valve (10). The first filter (3) is arranged on the oil inlet pipeline of the first oil pump (5) and the second oil pump (9), the second filter (7) is arranged on the oil outlet pipeline of the first oil pump (5), and the third filter (11) is arranged on the oil outlet pipeline of the second oil pump (9); the first filter (3) is connected in parallel with the first differential pressure switch (4), the second filter (7) is connected in parallel with the second differential pressure switch (8), and the third filter (11) is connected in parallel with the third differential pressure switch (12). The first oil pump (5) is connected in parallel with the first check valve (6), the oil inlet of the first check valve (6) is communicated with the oil outlet of the first oil pump (5), and the oil outlet of the first check valve (6) is communicated with the oil inlet of the first oil pump (5). The second oil pump (9) is connected with a second check valve (10) in parallel, an oil inlet of the second check valve (10) is communicated with an oil outlet of the second oil pump (9), and an oil outlet of the second check valve (10) is communicated with an oil inlet of the second oil pump (9).

6. The hydraulic control system for a powershift transmission as set forth in claim 4, wherein, The main control module A further comprises a second pressure regulating valve (14), an oil inlet of the second pressure regulating valve (14) is connected with an input oil path b of the torque converter, and an oil outlet of the second pressure regulating valve (14) is connected with the oil suction path u.

7. The hydraulic control system for a powershift transmission as set forth in claim 5, wherein, An oil inlet pipeline of the first filter (3) is provided with a temperature sensor (2), and the temperature sensor (2) is connected with an oil return path c.

8. A powershift transmission characterized by The power shift transmission is provided with the hydraulic control system for the power shift transmission as claimed in any one of claims 1-7.

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