Hydraulic retarder output torque characteristic self-optimization control system and vehicle

Abstract

The invention discloses a hydraulic retarder output torque characteristic self-optimization control system and a vehicle. The system comprises an oil suction one-way valve, a pilot piston cavity, a working cavity rapid oil drain valve, a low-rotating-speed pressurizing valve, a high-rotating-speed pressure release valve, a main oil duct pressure release valve, a working state switching valve, a retarder body, an oil pump and a working medium container. The retarder body comprises a stator and a rotor, and the rotor and the oil pump are fixedly connected with a whole vehicle transmission shaft through a transmission structure and rotate synchronously. The air inlet end of the working state switching valve is connected with an air source, and the air outlet end of the working state switching valve is connected with the pilot piston cavity, the working cavity quick oil drain valve and a control cavity of the main oil duct pressure release valve in three ways to control on-off, so that oil inlet quantity and pressure adjustment of the working cavity of the retarder body at different rotating speeds are achieved.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic retarder technology, specifically relating to a self-optimizing control system for the output torque characteristics of a hydraulic retarder and a vehicle. Background Technology

[0002] Hydraulic retarders, as important auxiliary braking devices for vehicles, are widely used in commercial vehicles such as trucks. They achieve braking through fluid damping, effectively reducing the number of braking maneuvers when driving downhill, lowering the wear rate of brake pads, and significantly reducing the operating temperature of wheel hubs, thereby improving vehicle safety. Therefore, they have gained widespread recognition from vehicle manufacturers and end users. As the market penetration rate of hydraulic retarders gradually increases, users are placing more stringent demands on their braking performance.

[0003] However, due to the limitations of its own structure and mechanical characteristics, existing conventional hydraulic retarders have inherent defects in the matching characteristics of output braking torque and rotor speed under the same input parameters: the output braking torque does not increase monotonically with the increase of rotor speed. When the rotor speed exceeds a certain critical value, the braking torque will decrease with the further increase of speed. This characteristic makes it difficult to adapt to the complex driving conditions of vehicles.

[0004] From the perspective of practical application needs, current users' core performance requirements for hydraulic retarders specifically include: First, higher output torque in the low-speed range to ensure significant braking effect over a wide speed range; Second, after the output torque reaches its maximum value, it can maintain stable torque output within a certain speed range, ensuring the smoothness and control accuracy of braking torque under high-speed conditions, and improving user comfort; Third, shorter activation response time, that is, after triggering the braking command, the output torque can quickly reach the target torque value.

[0005] In summary, the braking torque output characteristics of existing hydraulic retarders can no longer meet the ever-increasing performance requirements of users. Summary of the Invention

[0006] The purpose of this invention is to provide a self-optimizing control system and vehicle for the output torque characteristics of a hydraulic retarder, in order to solve the technical defects of existing hydraulic retarders in the prior art, such as insufficient torque at low speeds, decreased torque at high speeds with increasing speed and poor stability, and slow opening response.

[0007] The technical solution adopted in this invention is as follows: A first aspect of this application provides a self-optimizing control system for the output torque characteristics of a hydraulic retarder, comprising: Oil suction check valve, pilot piston chamber, working chamber quick oil discharge valve, low speed pressurization valve, high speed pressure relief valve, main oil passage pressure relief valve, working state switching valve, retarder body, oil pump and working medium container; The retarder body includes a stator and a rotor. The rotor is fixedly connected to the vehicle drive shaft and rotates synchronously with the oil pump through a transmission structure. The working state switching valve is connected to an air source at its inlet end and to a control chamber of the pilot piston chamber, the working chamber quick oil drain valve, and the main oil passage pressure relief valve via three separate air outlets to control the on / off state. The pilot piston chamber has an oil inlet end connected in series with an oil suction check valve and an oil outlet end connected to the working chamber of the retarder body to achieve rapid oil injection. The oil pump inlet is connected to the working medium container, and the outlet is connected to the retarder body working chamber via the oil supply pipeline. The low-speed pressurization valve and the high-speed pressure relief valve are both connected in series to the oil supply pipeline, and the main oil passage pressure relief valve is connected in series to the main oil passage to achieve the adjustment of the oil inlet volume and pressure of the retarder body working chamber at different speeds.

[0008] In one optional embodiment, the oil inlet of the suction check valve is connected to the oil outlet of the working medium container, and the oil outlet is connected to the oil inlet of the pilot piston chamber, so that the oil can only flow from the working medium container to the pilot piston chamber in one direction and prevent the oil from flowing back in the opposite direction.

[0009] In one optional embodiment, the low-speed pressurization valve is a normally closed pressure control valve, and its opening pressure is set to a first preset threshold. The oil pump automatically starts when the output pressure reaches the first preset threshold, thereby increasing the oil flow rate and oil pressure in the working chamber of the retarder body.

[0010] In one optional embodiment, the high-speed pressure relief valve is a normally closed pressure control valve, and its opening pressure is set to a second preset threshold, which is greater than a first preset threshold. When the oil pump output pressure reaches the second preset threshold, it will automatically turn on to divert part of the oil to the system return oil pipeline.

[0011] In one optional embodiment, the working state switching valve is a solenoid valve, whose signal input terminal is electrically connected to the vehicle controller, receives the current signal output by the controller, and controls the action range of the pilot piston chamber, the working chamber quick oil drain valve and the main oil passage pressure relief valve by adjusting the output air pressure.

[0012] In one optional embodiment, a filter is connected in series in the oil supply line. The oil inlet of the filter is connected to the oil outlet of the oil pump, and the oil outlet is connected to the oil inlet of the low-speed pressure valve, for filtering out solid impurities in the oil.

[0013] In an optional embodiment, a heat exchanger is further included, which is connected in series to the oil return line of the retarder working chamber. The oil inlet of the heat exchanger is connected to the oil outlet of the retarder working chamber, and the oil outlet is connected to the working medium container, for cooling the oil that has heated up after operation.

[0014] In one optional embodiment, an oil drain check valve is connected in series at the oil outlet end of the retarder working chamber, and the oil inlet end of the oil drain check valve is connected to the oil outlet end of the retarder working chamber. The oil outlet of the one-way valve is connected to the oil inlet of the heat exchanger to block the backflow of oil and increase the oil pressure in the working chamber of the retarder.

[0015] In one optional embodiment, the transmission structure is a coupling or a gear transmission assembly. The power input end of the transmission structure is fixedly connected to the vehicle drive shaft, and the power output end is connected to the power input ends of the rotor and the oil pump, respectively, so as to realize synchronous rigid transmission between the rotor, the oil pump and the vehicle drive shaft.

[0016] A second aspect of this application provides a vehicle comprising: The frame, wheels, transmission system, and the hydraulic retarder output torque characteristic self-optimization control system as described above; The transmission system includes a drive shaft, and the retarder body rotor and oil pump of the hydraulic retarder output torque characteristic self-optimization control system are fixedly connected to the drive shaft through a transmission structure. The hydraulic retarder output torque characteristic self-optimization control system is used to brake and decelerate the vehicle during driving, and achieves self-optimization of output torque characteristics by adapting the oil supply and pressure adjustment of the retarder working chamber at different speeds.

[0017] Compared with the prior art, the present invention has the following beneficial effects: The low-speed pressure-boosting valve connected in series in the oil supply line can specifically increase the oil inlet pressure and flow rate of the retarder working chamber under low-speed conditions, directly solving the defect of insufficient low-speed torque in conventional retarders and ensuring significant braking effect over a wide speed range. The high-speed pressure relief valve and the main oil passage pressure relief valve work together to automatically adjust the working chamber pressure after the speed exceeds the critical value, preventing the torque from decreasing as the speed increases, achieving stable output in the peak torque range, improving control accuracy and user comfort. The rapid oil injection structure composed of the pilot piston chamber and the oil suction check valve, combined with the precise air circuit control of the working state switching valve, can quickly replenish oil to the working chamber after the braking command is triggered, significantly shortening the torque response time. The rotor and oil pump are fixedly connected to the drive shaft for synchronous linkage, and the coordinated control of multiple valves can adaptively optimize torque characteristics according to the overall vehicle operating conditions, without the need for additional drive components, resulting in strong adaptability and reliability. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A schematic diagram illustrating the application of a self-optimizing control system for the output torque characteristics of a hydraulic retarder provided by this invention; Figure 2 A schematic diagram illustrating the application effect of a self-optimizing control system for the output torque characteristics of a hydraulic retarder provided by the present invention; In the diagram: 1. Air source; 2. Oil suction check valve; 3. Pilot piston chamber; 4. Filter; 5. Oil pump; 6. Working chamber quick drain valve; 7. Retarder stator; 8. Retarder rotor; 9. Low-speed pressurization valve; 10. Oil discharge check valve; 11. High-speed pressure relief valve; 12. Heat exchanger; 13. Main oil passage pressure relief valve; 14. Working medium container; 15. Working state switching valve; 16. Retarder working chamber; 17. Working chamber oil outlet passage; 18. Low-speed oil inlet passage; 19. Front-end oil pump output passage; 20. Heat exchanger oil inlet passage; 21. Medium-speed oil inlet passage; 22. Heat exchanger oil outlet passage. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0021] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0022] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0023] To address the technical deficiencies mentioned in the background section, the present invention will now be described in further detail with reference to the accompanying drawings: like Figures 1-2As shown, in the first aspect of this application, a self-optimizing control system for the output torque characteristics of a hydraulic retarder is provided, comprising: a suction check valve 2, a pilot piston chamber 3, a working chamber quick-release valve 6, a low-speed pressurization valve 9, a high-speed pressure relief valve 11, a main oil passage pressure relief valve 13, a working state switching valve 15, a retarder body, an oil pump 5, and a working medium container 14; the retarder body includes a stator 7 and a rotor 8, the rotor 8 and the oil pump 5 are fixedly connected to the vehicle drive shaft through a transmission structure and rotate synchronously; the working state switching valve 15 has an air source 1 at its inlet end and three outlet ends. The control chamber of the pilot piston chamber 3, the working chamber quick-release valve 6, and the main oil passage pressure relief valve 13 are connected to control the on / off state. The oil inlet end of the pilot piston chamber 3 is connected in series with the suction check valve 2, and the oil outlet end is connected to the working chamber 16 of the retarder body to achieve rapid oil injection. The oil pump 5 is connected to the working medium container 14 at the oil inlet end and to the working chamber 16 of the retarder body via the oil supply pipeline. The low-speed pressurization valve 9 and the high-speed pressure relief valve 11 are both connected in series with the oil supply pipeline. The main oil passage pressure relief valve 13 is connected in series with the main oil passage to achieve the adjustment of the oil inlet volume and pressure of the working chamber 16 of the retarder body at different speeds.

[0024] In the above structure, the low-speed pressure valve 9 connected in series in the oil supply line can specifically increase the oil inlet pressure and flow rate of the retarder working chamber 16 under low-speed conditions, directly solving the defect of insufficient low-speed torque of conventional retarders and ensuring significant braking effect over a wide speed range; the high-speed pressure relief valve 11 and the main oil passage pressure relief valve 13 work together to automatically adjust the pressure of the working chamber 16 after the speed exceeds the critical value, preventing the torque from decreasing as the speed increases, achieving stable output in the peak torque range, and improving control accuracy and user comfort; the rapid oil injection structure composed of the pilot piston chamber 3 and the oil suction check valve 2, combined with the precise air circuit control of the working state switching valve 15, can quickly replenish oil to the working chamber 16 after the braking command is triggered, significantly shortening the torque response time; the rotor 8 and the oil pump 5 are fixedly connected to the drive shaft to achieve synchronous linkage, and the multi-valve coordinated control can adaptively optimize the torque characteristics according to the overall vehicle working conditions, without the need for additional drive components, and has strong adaptability and reliability.

[0025] In this embodiment, the oil inlet of the suction check valve 2 is connected to the oil outlet of the working medium container 14, and the oil outlet is connected to the oil inlet of the pilot piston chamber 3, so that the oil can only flow from the working medium container 14 to the pilot piston chamber 3 in one direction, and the reverse flow of the oil is blocked.

[0026] In this embodiment, the low-speed pressurization valve 9 is a normally closed pressure control valve, and its opening pressure is set to a first preset threshold. When the output pressure of the oil pump 5 reaches the first preset threshold, it automatically opens to increase the oil flow rate and oil pressure in the working chamber 16 of the retarder body. The high-speed pressure relief valve 11 is a normally closed pressure control valve, and its opening pressure is set to a second preset threshold, which is greater than the first preset threshold. When the output pressure of the oil pump 5 reaches the second preset threshold, it automatically opens to divert some oil to the system return oil pipeline.

[0027] Furthermore, the working state switching valve 15 is a solenoid valve, whose signal input terminal is electrically connected to the vehicle controller, receives the current signal output by the controller, and controls the action range of the pilot piston chamber 3, the working chamber quick oil drain valve 6 and the main oil passage pressure relief valve 13 by adjusting the output air pressure. A filter 4 is connected in series in the oil supply line. The oil inlet of the filter 4 is connected to the oil outlet of the oil pump 5, and the oil outlet is connected to the oil inlet of the low speed pressure valve 9, which is used to filter out solid impurities in the oil.

[0028] In this embodiment, a heat exchanger 12 is also included. The heat exchanger 12 is connected in series to the oil return line of the retarder working chamber 16. Its oil inlet end is connected to the oil outlet end of the retarder working chamber 16, and the oil outlet end is connected to the working medium container 14, which is used to cool down the oil that has heated up after working.

[0029] An oil drain check valve 10 is connected in series at the oil outlet end of the retarder working chamber 16. The oil inlet end of the oil drain check valve 10 is connected to the oil outlet end of the retarder working chamber 16. The oil outlet end of the oil drain check valve 10 is connected to the oil inlet end of the heat exchanger 12 to block the reverse flow of oil and increase the oil pressure in the retarder working chamber 16.

[0030] In this embodiment, the transmission structure is a coupling or a gear transmission assembly. The power input end of the transmission structure is fixedly connected to the vehicle's drive shaft, and the power output end is connected to the power input ends of the rotor 8 and the oil pump 5, respectively, so as to realize synchronous rigid transmission between the rotor 8, the oil pump 5 and the vehicle's drive shaft.

[0031] When the hydraulic retarder starts working, the working state switching valve 15 opens, and high-pressure air is output from the air source 1 and enters the retarder system in two paths: one path of high-pressure air enters the pilot piston chamber 3. Since the oil cannot pass through the oil suction check valve 2, the oil in the pilot piston chamber 3 enters the space between the retarder stator 7 and the retarder rotor 8 through the oil inlet passage, providing oil to the retarder working chamber 16 (retarder stator 7 and retarder rotor 8) at the fastest speed, generating braking torque and improving the response time from receiving the working signal to the retarder output torque.

[0032] Another high-pressure gas enters the two valve working chambers' quick-release valve 6 and main oil passage pressure relief valve 13, causing the quick-release valve 6 in the working chamber to close and the main oil passage pressure relief valve 13 to close. At this time, the retarder's working oil passage is in a complete circulation state, and internal pressure can be built up to generate torque. The oil in the working medium container 14, under the action of the oil pump 5, is filtered by the filter 4 and enters the front oil pump output oil passage 19 at the front end of the retarder working chamber 16.

[0033] At this point, the following situations may occur. First, when the retarder rotor 8 of the hydraulic retarder rotates at a low speed (usually below 300 rpm), the output flow and pressure of the oil pump 5 are low. The low-speed pressurization valve 9 and the high-speed pressure relief valve 11 cannot open, and the oil can only flow from... Figure 1 The low-speed oil inlet 18 on the upper side of the stator 7 of the medium retarder enters the working chamber 16 of the retarder.

[0034] In the second scenario, when the retarder rotor 8 of the hydraulic retarder is at a medium speed (usually in the range of 300~1100 rpm), the output flow and pressure of the oil pump 5 increase relatively. The low-speed pressure valve 9 opens, while the high-speed pressure relief valve 11 cannot open. Oil can enter simultaneously from the low-speed oil inlet 18 and the medium-speed oil inlet 21 on the retarder stator 7. The amount of oil entering the retarder working chamber 16 increases compared to the first scenario.

[0035] According to the performance curve of the hydraulic retarder, the retarder's output torque is very small at extremely low speeds. The low-speed pressure valve 9 is designed to open only when the retarder rotor 8 rotates above 300 rpm. This increases the inlet pressure of the retarder's working chamber 16, thereby increasing the retarder's output torque, while minimizing the impact on the low-speed torque of the hydraulic retarder, thus achieving a significant increase in low-speed torque over a wide range.

[0036] The third scenario involves the retarder rotor 8 rotating at high speed (above 1100 rpm). At this speed, the output flow and pressure of the retarder oil pump 5 increase significantly. Both the low-speed pressurization valve 9 and the high-speed relief valve 11 are open. While oil can enter through the low-speed oil inlet 18 and the medium-speed oil inlet 21 on the retarder stator 7, some oil will pass through the high-speed relief valve 11 and return to the heat exchanger 12 directly through the heat exchanger oil inlet 20 without passing through the retarder working chamber 16. This results in a reduction in the amount of oil entering the retarder working chamber 16 compared to the second scenario.

[0037] After the oil pump 5 outputs oil into the space between the retarder stator 7 and the retarder rotor 8 through the three methods described above, the retarder rotor 8 agitates the oil, acting on the retarder stator 7, and the oil reacts on the retarder rotor 8, thereby generating braking torque. The drain check valve 10 increases the oil pressure between the retarder stator 7 and the retarder rotor 8, enhancing the braking torque. The braking torque is transmitted to the vehicle's drivetrain through the rotor, achieving the effect of reducing vehicle speed. After the oil generates braking torque, its temperature rises. It then enters the heat exchanger 12 through the working chamber oil outlet 17, the drain check valve 10, and the heat exchanger inlet 20, where it is cooled by circulating cooling water. Afterward, it returns to the space between the retarder stator 7 and the retarder rotor 8 through the heat exchanger outlet 22, forming a complete oil circulation, allowing the retarder to continuously generate torque.

[0038] In summary, the oil circulation path of the hydraulic retarder varies depending on the rotational speed: when the rotational speed is low (usually below 300 rpm), the circulation path is as follows: the working medium container 14 delivers the oil to the filter 4, and then the oil pump 5 delivers it to the retarder working chamber 16. The retarder working chamber 16 is connected to the heat exchanger 12 through the working chamber oil outlet 17 and the low-speed oil inlet 18. The retarder working chamber 16 is also connected to the heat exchanger 12 through the heat exchanger oil outlet 22.

[0039] When the speed is at medium speed (usually in the range of 300~1100 rpm), the circulating oil passage is as follows: the working medium container 14 delivers the oil to the filter 4, and then the oil pump 5 delivers it to the low speed oil inlet 18 and the medium speed oil inlet 21. The oil inlet 18 and the medium speed oil inlet 21 deliver the oil to the retarder working chamber 16. The retarder working chamber 16 is connected to the heat exchanger 12 through the working chamber oil outlet 17 and the low speed oil inlet 18. The heat exchanger oil outlet 22 is also connected between the retarder working chamber 16 and the heat exchanger 12.

[0040] When the speed is high (usually above 1100 rpm), the circulating oil passage is as follows: the working medium container 14 delivers the oil to the filter 4, and then the oil pump 5 delivers it to the low-speed oil inlet 18 and the medium-speed oil inlet 21. The oil inlet 18 and the medium-speed oil inlet 21 deliver the oil to the retarder working chamber 16. The retarder working chamber 16 is connected to the heat exchanger 12 through the working chamber oil outlet 17 and the low-speed oil inlet 18. The retarder working chamber 16 is also connected to the heat exchanger 12 through the heat exchanger oil outlet 22, and the oil pump 5 is also connected to the heat exchanger 12 through the heat exchanger oil inlet 20.

[0041] When the hydraulic retarder disengages, the controller sends a signal to close the operating state switching valve 15, releasing the air pressure from the air chamber of the pilot piston chamber 3. The high-pressure oil in the heat exchanger oil outlet 22 pushes the piston, and the oil in the working medium container 14 enters the pilot piston chamber 3 through the suction check valve 2, preparing for the next retarder operation. Simultaneously, the working chamber quick-release valve 6 and the main oil passage pressure relief valve 13 switch to the open state, allowing the oil in the retarder working chamber 16 to be quickly discharged into the working medium container 14. The oil in the main oil passage flows out of the heat exchanger 12 and enters the working medium container 14. The entire retarder enters a low-pressure state, no longer generating braking torque, and the hydraulic retarder disengages.

[0042] In a second aspect of this application, a vehicle is provided, including: a frame, wheels, a transmission system, and a hydraulic retarder output torque characteristic self-optimization control system as described above; the transmission system includes a drive shaft, and the retarder body rotor 8 of the hydraulic retarder output torque characteristic self-optimization control system and the oil pump 5 are fixedly connected to the drive shaft through a transmission structure; the hydraulic retarder output torque characteristic self-optimization control system is used to brake and decelerate the vehicle during driving, and to achieve self-optimization of output torque characteristics by adjusting the oil supply and pressure of the retarder working chamber 16 at different speeds.

[0043] 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 self-optimizing control system for the output torque characteristics of a hydraulic retarder, characterized in that, include: Oil suction check valve, pilot piston chamber, working chamber quick oil discharge valve, low speed pressurization valve, high speed pressure relief valve, main oil passage pressure relief valve, working state switching valve, retarder body, oil pump and working medium container; The retarder body includes a stator and a rotor. The rotor is fixedly connected to the vehicle drive shaft and rotates synchronously with the oil pump through a transmission structure. The working state switching valve is connected to an air source at its inlet end and to a control chamber of the pilot piston chamber, the working chamber quick oil drain valve, and the main oil passage pressure relief valve via three separate air outlets to control the on / off state. The pilot piston chamber has an oil inlet end connected in series with an oil suction check valve and an oil outlet end connected to the working chamber of the retarder body to achieve rapid oil injection. The oil pump inlet is connected to the working medium container, and the outlet is connected to the retarder body working chamber via the oil supply pipeline. The low-speed pressurization valve and the high-speed pressure relief valve are both connected in series to the oil supply pipeline, and the main oil passage pressure relief valve is connected in series to the main oil passage to achieve the adjustment of the oil inlet volume and pressure of the retarder body working chamber at different speeds.

2. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 1, characterized in that, The oil inlet of the suction check valve is connected to the oil outlet of the working medium container, and the oil outlet is connected to the oil inlet of the pilot piston chamber, so that the oil can only flow from the working medium container to the pilot piston chamber in one direction and prevent the oil from flowing back in the opposite direction.

3. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 1, characterized in that, The low-speed pressurization valve is a normally closed pressure control valve, and its opening pressure is set to a first preset threshold. The oil pump automatically starts when the output pressure reaches the first preset threshold, thereby increasing the oil flow rate and oil pressure in the working chamber of the retarder body.

4. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 3, characterized in that, The high-speed pressure relief valve is a normally closed pressure control valve, and its opening pressure is set to a second preset threshold, which is greater than the first preset threshold. When the oil pump output pressure reaches the second preset threshold, it will automatically turn on to divert part of the oil to the system return oil pipeline.

5. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 1, characterized in that, The working state switching valve is a solenoid valve. Its signal input terminal is electrically connected to the vehicle controller, receives the current signal output by the controller, and controls the movement range of the pilot piston chamber, the working chamber quick oil drain valve and the main oil passage pressure relief valve by adjusting the output air pressure.

6. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 1, characterized in that, A filter is connected in series in the oil supply line. The oil inlet of the filter is connected to the oil outlet of the oil pump, and the oil outlet is connected to the oil inlet of the low-speed pressure valve. The filter is used to filter out solid impurities in the oil.

7. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 1, characterized in that, It also includes a heat exchanger, which is connected in series to the oil return line of the retarder working chamber. Its oil inlet end is connected to the oil outlet end of the retarder working chamber, and the oil outlet end is connected to the working medium container, which is used to cool down the oil that has heated up after working.

8. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 7, characterized in that, An oil drain check valve is connected in series at the oil outlet end of the retarder working chamber, and the oil inlet end of the oil drain check valve is connected to the oil outlet end of the retarder working chamber. The oil outlet of the one-way valve is connected to the oil inlet of the heat exchanger to block the backflow of oil and increase the oil pressure in the working chamber of the retarder.

9. The self-optimizing control system for the output torque characteristics of a hydraulic retarder according to claim 1, characterized in that, The transmission structure is a coupling or a gear transmission assembly. The power input end of the transmission structure is fixedly connected to the vehicle's drive shaft, and the power output end is connected to the power input ends of the rotor and the oil pump, respectively, so as to realize synchronous rigid transmission between the rotor, the oil pump and the vehicle's drive shaft.

10. A vehicle, characterized in that, include: A chassis, wheels, a transmission system, and a self-optimizing control system for the output torque characteristics of a hydraulic retarder as described in any one of claims 1-9; The transmission system includes a drive shaft, and the retarder body rotor and oil pump of the hydraulic retarder output torque characteristic self-optimization control system are fixedly connected to the drive shaft through a transmission structure. The hydraulic retarder output torque characteristic self-optimization control system is used to brake and decelerate the vehicle during driving, and achieves self-optimization of output torque characteristics by adapting the oil supply and pressure adjustment of the retarder working chamber at different speeds.

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