System proportional pressure regulating valve and hydraulic control system

Abstract

The utility model discloses a system proportional pressure regulating valve and a hydraulic control system, the system proportional pressure regulating valve comprises a valve body, a sliding chute is arranged in the valve body, and the valve body is sequentially provided with a first port, a second port, a third port, a fourth port and a fifth port; the valve element is arranged in the sliding groove in a sliding mode, the outer surface of the valve element and the inner surface of the sliding groove are in sealing fit, and a first communicating groove and a second communicating groove are sequentially formed in the outer surface of the valve element in the axis direction of the valve element; the elastic piece is connected with the valve element so that the valve element can elastically reciprocate in the sliding groove. Compared with the prior art, the system proportional pressure regulating valve has the advantages that multiple functions are achieved through one valve, the functions of pressure regulation, safety protection and one-way flowing are achieved, the number of mechanical valves in the hydraulic valve plate is reduced, the failure rate is reduced, and the hardware cost is reduced; the external dimension of the hydraulic valve plate is reduced to the maximum extent, redundant space of a gearbox is not occupied, and layout of the whole gearbox is facilitated.

Description

TECHNICAL FIELD

[0001] The utility model relates to vehicle hydraulic control system technical field, especially a system proportional pressure regulating valve and hydraulic control system. BACKGROUND

[0002] At present, the P1+P3 architecture double-motor hybrid gearbox developed by various companies on the market, P1 motor is mainly used for power generation, and P3 motor is mainly used for driving. The role of the hydraulic system in the hybrid gearbox is mainly to provide high-pressure execution oil for the clutch required for gear shifting, to provide cooling oil for the motor heat dissipation, and to provide lubricating oil for the clutch and gear shaft system. However, the technical route of the hydraulic system design is different, mainly in the selection type of hydraulic integrated valve plate and hydraulic power source.

[0003] The hydraulic valve plate in the prior art has complex principle, many hydraulic mechanical valves, high theoretical mechanical failure rate, large appearance size of the hydraulic valve plate, and occupies much space, which affects the overall structure layout. INVENTION CONTENTS

[0004] The utility model aims at providing a system proportional pressure regulating valve and hydraulic control system to solve the technical problems in the prior art, which can simplify the structure of the hydraulic valve plate.

[0005] The utility model provides a system proportional pressure regulating valve, which comprises:

[0006] A valve body is provided with a sliding groove, and a first port, a second port, a third port, a fourth port and a fifth port are sequentially arranged on the valve body along the extension direction of the sliding groove;

[0007] A valve core is slidably arranged in the sliding groove, and a sealing fit is formed between the outer surface of the valve core and the inner surface of the sliding groove. First and second communication grooves are sequentially arranged on the outer surface of the valve core along the axial direction of the valve core;

[0008] An elastic member is arranged in the sliding groove and connected with the valve core, so that the valve core can elastically reciprocate in the sliding groove;

[0009] Among them:

[0010] The valve core has a first end and a second end, a first chamber is formed between the first end face of the valve core and the inner surface of the sliding groove, the first port is in communication with the first chamber, and a second chamber is formed between the second end face of the valve core and the inner surface of the sliding groove, the second port is in communication with the second chamber;

[0011] The valve core has a first interval and a second interval on a moving path of the valve core, the first interval and the second interval have a partially overlapped area, only in the first interval, the second port is communicated with the fourth port through the first communication groove, and only in the second interval, the third port is communicated with the second port through the second communication groove.

[0012] The system proportional pressure regulating valve as claimed in any one of the preceding claims, wherein preferably, an end surface area of the first end of the valve core is smaller than an end surface area of the second end of the valve core.

[0013] The system proportional pressure regulating valve as claimed in any one of the preceding claims, wherein preferably, the elastic member comprises a spring arranged in the second chamber, and opposite ends of the spring are respectively abutted against the second end of the valve core and an inner wall surface of the sliding groove.

[0014] In a second aspect, the utility model provides a kind of hydraulic control system, including first pump body, second pump body, system proportional pressure regulating valve, first electromagnetic valve, second electromagnetic valve, third electromagnetic valve, fourth electromagnetic valve and first pressure sensor, the system proportional pressure regulating valve is the system proportional pressure regulating valve of preceding, wherein:

[0015] The liquid outlet of the first pump body is respectively communicated to the first port and the third port of the system proportional pressure regulating valve, the liquid inlet of the first electromagnetic valve, the liquid inlet of the second electromagnetic valve, the liquid inlet of the third electromagnetic valve and the first pressure sensor;

[0016] The liquid outlet of the second pump body is communicated to P3 motor by first pipeline, the first pipeline is communicated with second pipeline, the second pipeline is communicated to P1 motor, and the fourth electromagnetic valve is arranged on the second pipeline;

[0017] The fourth port of the system proportional pressure regulating valve is communicated to the second pipeline;

[0018] The liquid outlet of the first electromagnetic valve is communicated to the fifth port of the system proportional pressure regulating valve;

[0019] The liquid outlet of the second electromagnetic valve is communicated to first clutch;

[0020] The liquid outlet of the third electromagnetic valve is communicated to second clutch.

[0021] The hydraulic control system as claimed in any one of the preceding claims, wherein preferably, the first pump body is a mechanical pump, and the second pump body is an electronic oil pump.

[0022] The hydraulic control system as claimed in any one of the preceding claims, wherein preferably, the first pump body is communicated to an oil pan through a third pipeline, an oil suction filter is arranged on the third pipeline, and the second pump body is communicated to the third pipeline through a fourth pipeline, and the fourth pipeline is communicated to the third pipeline between the oil suction filter and the first pump body.

[0023] The hydraulic control system as claimed in any one of the preceding claims, wherein preferably, the liquid outlet end of the first pump body is communicated to the liquid inlet end of a high-pressure filter, and the liquid outlet end of the high-pressure filter is respectively communicated to the first port and the third port of the system proportional pressure regulating valve, the liquid inlet end of the first electromagnetic valve, the liquid inlet end of the second electromagnetic valve, the liquid inlet end of the third electromagnetic valve, and the first pressure sensor.

[0024] The hydraulic control system as claimed in any one of the preceding claims, wherein preferably, a one-way valve, an oil cooler and a fine filter are arranged on the first pipeline in sequence, and the second pipeline is communicated to the first pipeline between the fine filter and the P3 motor.

[0025] The hydraulic control system as claimed in any one of the preceding claims, wherein preferably, a first accumulator and a second pressure sensor are arranged on the pipeline between the second electromagnetic valve and the first clutch.

[0026] The hydraulic control system as claimed in any one of the preceding claims, wherein preferably, a second accumulator and a third pressure sensor are arranged on the pipeline between the third electromagnetic valve and the second clutch.

[0027] Compared with the prior art, the system proportional pressure regulating valve provided by the utility model realizes the multi-function of one valve, meets the functions of pressure regulating, safety protection and one-way flow, reduces the number of mechanical valves in the hydraulic valve plate, reduces the failure rate, reduces the hardware cost, maximally reduces the appearance size of the hydraulic valve plate, does not occupy the redundant space of the gearbox, is favorable to the layout of the whole gearbox. BRIEF DESCRIPTION OF DRAWINGS

[0028] Figure 1 is the sectional view of the system proportional pressure regulating valve provided by the utility model embodiment;

[0029] Figure 2 is the system principle diagram of the hydraulic control system provided by the utility model embodiment.

[0030] EXPLANATION OF REFERENCE NUMERALS:

[0031] 1 - system proportional pressure regulating valve, 101 - valve body, 102 - sliding groove, 103 - first port, 104 - second port, 105 - third port, 106 - fourth port, 107 - fifth port, 108 - valve core, 109 - first communication groove, 110 - second communication groove, 111 - elastic member, 112 - first chamber, 113 - second chamber, 114 - baffle, 115 - end plug, 116 - first positioning groove, 117 - second positioning groove;

[0032] 2 - first pump body, 3 - second pump body, 4 - first electromagnetic valve, 5 - second electromagnetic valve, 6 - third electromagnetic valve, 7 - fourth electromagnetic valve, 8 - P1 motor, 9 - P3 motor, 10 - first clutch, 11 - second clutch, 12 - oil sump, 13 - oil suction filter, 14 - check valve, 15 - oil cooler, 16 - fine filter, 17 - high pressure filter, 18 - first pressure sensor, 19 - first accumulator, 20 - second pressure sensor, 21 - second accumulator, 22 - third pressure sensor, 23 - first pipeline, 24 - second pipeline, 25 - third pipeline, 26 - fourth pipeline. DETAILED DESCRIPTION

[0033] The embodiments of the present application will be described in detail below, examples of which are shown in the drawings, wherein the same or similar notations represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by reference to the drawings are exemplary only, and are used only for explaining the present application, and cannot be interpreted as a limitation of the present application.

[0034] In a first aspect, as Figure 1 The embodiments of the present application provide a system proportional pressure regulating valve 1 to be applied to a hydraulic valve plate in a hydraulic control system of a vehicle, to realize pressure regulating, safety protection and one-way flow functions, thereby reducing the number of mechanical valves in the hydraulic valve plate and reducing the appearance size of the hydraulic valve plate. In a feasible implementation manner, the system proportional pressure regulating valve 1 comprises a valve body 101, a valve core 108 and an elastic member 111, wherein:

[0035] The valve body 101 is provided with a sliding groove 102 for accommodating a valve core 108, and the sliding of the valve core 108 controls the on-off state of each port. Along the extension direction of the sliding groove 102, the valve body 101 is linearly arranged with a first port 103, a second port 104, a third port 105, a fourth port 106 and a fifth port 107 in sequence. The first port 103, the second port 104, the third port 105, the fourth port 106 and the fifth port 107 are respectively connected to the inside of the sliding groove 102 and the outside. In a feasible implementation, the first port 103, the third port 105 and the fifth port 107 are used for liquid inlet, the fourth port 106 is used for liquid outlet, and the second port 104 is used for liquid return. Thus, one valve can realize multiple functions such as liquid inlet, liquid outlet and liquid return, thereby reducing the number of mechanical valves in the hydraulic control system and simplifying the system structure.

[0036] The valve core 108 is slidably arranged in the sliding groove 102, and the outer surface of the valve core 108 is in sealing fit with the inner surface of the sliding groove 102. Thus, the valve core 108 can effectively isolate the liquids between different ports during sliding to prevent fluid leakage or cross talk. Along the axial direction of the valve core 108, the outer surface of the valve core 108 is provided with a first communication groove 109 and a second communication groove 110 in sequence. The communication grooves control the on-off relationship between different ports by the sliding of the valve core 108. When the valve core 108 slides to different positions, the communication grooves connect some ports and isolate other ports, thereby realizing the control of fluid flow direction.

[0037] Specifically, along the moving direction of the valve core 108, the end of the valve core 108 has a first end and a second end. The first end face of the valve core 108 and the inner surface of the sliding groove 102 form a first chamber 112 therebetween. The first port 103 is connected to the first chamber 112. After the fluid from the outside enters the first chamber 112, a first force is provided to the valve core 108. The direction of the first force is consistent with the sliding direction of the valve core 108, which pushes the valve core 108 to slide in the sliding groove 102 towards the second end. The second end face of the valve core 108 and the inner surface of the sliding groove 102 form a second chamber 113 therebetween. The second port 104 is connected to the second chamber 113. After the fluid from the outside enters the first chamber 112, a second force is provided to the valve core 108. The direction of the second force is consistent with the sliding direction of the valve core 108, which pushes the valve core 108 to slide in the sliding groove 102 towards the first port 103. The first force and the second force are opposite and different in size. This design makes the movement of the valve core 108 controllable by adjusting the pressure or flow of the fluid.

[0038] The valve core 108 has a first interval and a second interval on its moving path, and the first interval and the second interval have a partially overlapped area, so that the valve core 108 can belong to both the first interval and the second interval at some positions to achieve fluid path control, wherein:

[0039] Only in the first interval, the second port 104 is communicated with the fourth port 106 through the first communication groove 109, and fluid can flow from the third port 105 to the fourth port 106 through the first communication groove 109; only in the second interval, the third port 105 is communicated with the second port 104 through the second communication groove 110, and fluid can flow from the third port 105 to the second port 104 through the second communication groove 110; in the area where the first interval and the second interval overlap, after fluid enters from the third port 105, it flows to the fourth port 106 through the first communication groove 109 and to the second port 104 through the second communication groove 110, respectively; when the valve core 108 slides to other positions of the sliding groove 102, the first communication groove 109 and the second communication groove 110 are not connected to any port, thereby achieving isolation between the ports and preventing fluid flow.

[0040] The elastic member 111 is arranged in the sliding groove 102 and connected with the valve core 108, so that the valve core 108 can elastically move back and forth in the sliding groove 102 to achieve an automatic reset function of the valve core 108, which automatically resets the valve core 108 to the initial position after the external control signal disappears, to ensure the sealing and safety of the pressure regulating valve in the non-working state. At the same time, appropriate pre-tightening force is applied to the valve core 108 in different working states, so that the position of the valve core 108 is balanced with the system pressure or flow.

[0041] The system proportional pressure regulating valve 1 provided by the above embodiment is suitable for the following working conditions when applied in a hydraulic control system to achieve the functions of pressure regulation, safety protection and one-way flow:

[0042] In the first working condition, external fluid enters the first chamber 112 from the first port 103 to provide a first acting force to the valve core 108, at this time, the valve core 108 only needs to overcome the elastic force of the elastic member 111, at this time, the pressure value of the hydraulic control system is small, and the energy consumption is low, at this time, the valve core 108 is in the first interval, and fluid flows from the third port 105 to the fourth port 106 through the second communication groove 110 to perform a cooling and lubricating effect on the system.

[0043] When the system proportional pressure regulating valve 1 is in the second working condition, the first force increases, the valve core 108 of the system proportional pressure regulating valve 1 is continuously pushed to move towards the second end, the valve core 108 is located at the overlapping position of the first interval and the second interval, the fluid enters the third port 105, flows to the fourth port 106 through the first communication groove 109 and flows to the second port 104 through the second communication groove 110, so that the pressure limiting unloading is carried out and the components in the hydraulic control system are protected.

[0044] When the system proportional pressure regulating valve 1 is in the third working condition, the fluid enters the first chamber 112 from the first port 103 to provide the first force to the valve core 108, and the fluid enters the second chamber 113 from the fifth port 107 to provide the second force to the valve core 108, the first force and the second force dynamically adjust the opening size of the valve core 108 (the third port 105 to the fourth port 106 are conducted but throttled) to generate a pressure drop, when the forces on both ends of the valve core 108 reach dynamic balance, the stable value of the system pressure is obtained, and the system pressure can be accurately controlled in real time.

[0045] When the system proportional pressure regulating valve 1 is in the fourth working condition, the fluid enters the first communication groove 109 from the third port 105, pushes the valve core 108 to move, so that the valve core 108 enters the first interval, and the fluid flows from the first communication groove 109 to the fourth port 106.

[0046] In the embodiments provided by the utility model, the end surface area of the first end of the valve core 108 is smaller than the end surface area of the second end of the valve core 108, and the area difference is formed between the two ends. Figure 1 As shown in the figure, the cross-sectional area of the chute 102 in the region where the first chamber 112 is located is smaller than the cross-sectional area of the chute 102 in the region where the second chamber 113 is located, when the fluid exerts the same pressure, the force received by the second end (the area is larger) of the valve core 108 is greater than the force received by the first end (the area is smaller) of the valve core 108, the fluid pressure in the second chamber 113 can more effectively push the valve core 108 to move, so that the hydraulic control system pressure is amplified, so that the system can reach a higher working pressure under a lower control pressure, and the efficiency and response speed of the system are improved.

[0047] Preferably, the elastic member 111 comprises a spring arranged in the second chamber 113, and opposite ends of the spring are respectively abutted against the second end of the valve core 108 and the inner wall surface of the sliding groove 102, in a feasible implementation, a baffle 114 is arranged in the sliding groove 102, and a end plug 115 is fixed on the baffle 114, a first positioning groove 116 is arranged on the side of the end plug 115 away from the baffle 114, one end of the spring extends into the first positioning groove 116 and is fixed and positioned, thereby providing a stable positioning reference for the spring, a second positioning groove 117 is arranged on the end of the valve core 108 facing the end plug 115, and the other end of the spring extends into the second positioning groove 117, so that the spring always maintains stable connection during movement of the valve core 108 and cannot be loosened due to vibration or impact, and the elastic supporting effect of the spring can be reliably transmitted to the valve core 108, thereby ensuring the movement accuracy of the valve core 108 in the sliding groove 102, and thus the precise control of the fluid pressure and flow direction is realized.

[0048] The second chamber 113 is formed between the valve core 108 and the end plug 115, so that the system proportional pressure regulating valve 1 has the function of the one-way valve 14, and the fluid can only flow from the third port 105 to the fourth port 106, but cannot flow reversely. Figure 1 As shown in the left side of the fourth port 106, the third port 105 is not communicated with the fourth port 106, after the fluid enters the first communication groove 109 from the third port 105, the force applied by the fluid pushes the valve core 108 to move towards the end plug 115, after the first communication groove 109 reaches the position of the fourth port 106, the third port 105 and the fourth port 106 are communicated through the first communication groove 109, and the fluid can pass through the system proportional pressure regulating valve 1, at this time, the spring liquid is extruded to accumulate elastic restoring force, and after the force is weakened or disappears, the spring restoring force is released, thereby dynamically adjusting the flow of the fluid according to the change of the fluid pressure.

[0049] In the second aspect, referring to Figure 2 The utility model also provides a hydraulic control system, mainly responsible for providing high pressure execution oil liquid for the control of hybrid box double clutch, providing oil liquid for the cooling of motor, providing oil liquid for the lubrication of clutch and gear shaft system, specifically, the hydraulic control system comprises a first pump body 2, a second pump body 3, a system proportional pressure regulating valve 1, a first electromagnetic valve 4, a second electromagnetic valve 5, a third electromagnetic valve 6, a fourth electromagnetic valve 7 and a first pressure sensor 18, the system proportional pressure regulating valve 1 is the aforementioned system proportional pressure regulating valve 1, wherein:

[0050] The outlet end of the first pump body 2 is respectively communicated to the first port 103 and the third port 105 of the system proportional pressure regulating valve 1, the inlet end of the first electromagnetic valve 4, the inlet end of the second electromagnetic valve 5, the inlet end of the third electromagnetic valve 6 and the first pressure sensor 18, the first pump body 2 provides a main hydraulic oil source, the system proportional pressure regulating valve 1 is used for adjusting the pressure and flow direction of the hydraulic oil, the hydraulic oil pumped out by the first pump body 2 can flow into the first chamber 112 through the first port of the system proportional pressure regulating valve 1 to provide the first force for the valve core 108, the first electromagnetic valve 4, the second electromagnetic valve 5, the third electromagnetic valve 6 and the fourth electromagnetic valve 7 are used for controlling the on-off and flow direction of the hydraulic oil, and the first pressure sensor 18 is used for detecting the pressure of the hydraulic oil.

[0051] The outlet end of the second pump body 3 is communicated to the P3 motor 9 through the first pipeline 23, the first pipeline 23 is communicated with the second pipeline 24, the second pipeline 24 is communicated to the P1 motor 8, the fourth electromagnetic valve 7 is arranged on the second pipeline 24, and the hydraulic oil of the second pump body 3 can be provided to the P1 motor 8 and the P3 motor 9 at the same time, the fourth electromagnetic valve 7 is used for controlling the hydraulic oil supply of the P1 motor 8, the fourth electromagnetic valve 7 controls the on-off of the cooling flow of the P1 motor 8, saves the flow and reduces the energy consumption of the whole vehicle.

[0052] The fourth port 106 of the system proportional pressure regulating valve 1 is communicated to the second pipeline 24, so that the hydraulic oil pumped out by the first pump body 2 flows into the second pipeline 24 after passing through the system proportional pressure regulating valve 1, thereby providing the P1 motor 8 and the P3 motor 9. The outlet end of the first electromagnetic valve 4 is communicated to the fifth port 107 of the system proportional pressure regulating valve 1, so that the hydraulic oil pumped out by the first pump body 2 can flow into the second chamber 113 through the fifth port 107 of the system proportional pressure regulating valve 1 to provide the second force for the valve core 108.

[0053] The outlet end of the second electromagnetic valve 5 is communicated to the first clutch 10 to control the flow direction of the hydraulic oil to the first clutch 10, and the outlet end of the third electromagnetic valve 6 is communicated to the second clutch 11 to control the flow direction of the hydraulic oil to the second clutch 11.

[0054] The working mode of the hydraulic control system is:

[0055] When the engine is running, it corresponds to three working conditions of series connection, direct drive and parking power generation.

[0056] Firstly, the series connection working condition means that the engine drives the P1 motor 8 to generate electricity to supplement the battery, and the P3 motor 9 drives the vehicle to move forward, at this time, double motor cooling and full system lubrication are needed, the flow demand is large, and the first pump body 2 and the second pump body 3 work at the same time; the P1 motor 8 and the P3 motor 9 need to be cooled and radiated, the fourth electromagnetic valve 7 is electrified to be opened, and the second pump body 3 can adjust the speed according to the working condition demand to match the flow.

[0057] Secondly, the direct drive working condition refers to that the engine directly drives the vehicle to move forward, and the clutch needs to be engaged, at this time, the system pressure (the pressure at the outlet of the first pump body 2) needs to be adjusted to facilitate the clutch engagement control, the system pressure is adjusted by adjusting the current of the first electromagnetic valve 4, and then the current controls the second electromagnetic valve 5 and the third electromagnetic valve 6 to control the two drive gears respectively. In the direct drive working condition, since the P1 motor 8 and the P3 motor 9 do not work and do not generate heat, the cooling demand flow is small, and the hydraulic oil is mainly used for lubrication, at this time, the second pump body 3 can work for a long time or at a small speed.

[0058] Finally, in the parking power generation working condition, the fourth electromagnetic valve 7 is powered on to open for the P1 motor 8 cooling and heat dissipation, at this time, the second pump body 3 is controlled to work at a small speed or not work according to the working condition of the P1 motor 8.

[0059] When the engine is not started, it corresponds to the pure electric drive mode, at this time, the fourth electromagnetic valve 7 is not powered on, only the second pump body 3 needs to be started, at this time, the system proportional pressure regulating valve 1 is closed and can be used as the function of the one-way valve 14, so the rear end can not be provided with the one-way valve 14, thereby simplifying the structure. In the pure electric drive mode, only the P3 motor 9 cooling and system lubrication demand flow is required, different working conditions can be matched with the demand flow by adjusting the electronic pump speed, thereby avoiding the flow waste and saving the energy consumption.

[0060] In a feasible implementation manner, the first pump body 2 is a mechanical pump, and the second pump body 3 is an electronic oil pump, the combination of the mechanical pump and the electronic oil pump is adopted as the hydraulic power source, the mechanical pump provides the basic hydraulic oil flow, and the electronic oil pump can supplement or adjust the flow according to the actual demand, the electronic oil pump can be started and stopped and the speed can be adjusted according to different flow demands, the flow is dynamically adjusted according to the actual working condition, thereby avoiding the operation of the mechanical pump in the low efficiency working condition, and the energy consumption is significantly reduced, and the flow is adapted to save the energy consumption.

[0061] Further, the first pump body 2 is connected to the oil pan 12 through the third pipeline 25, the third pipeline 25 is provided with an oil suction filter 13, the second pump body 3 is connected to the third pipeline 25 through the fourth pipeline 26, and the connection position of the fourth pipeline 26 and the third pipeline 25 is located between the oil suction filter 13 and the first pump body 2. The first pump body 2 and the second pump body 3 both suck oil through the oil suction filter 13, the double-pump oil suction adopts one oil suction filter 13, the cost can be saved and the layout space can be reduced, the hydraulic oil is filtered before entering the two pump bodies, the oil suction filter 13 can filter out slightly large particles to prevent these impurities from entering the oil pump and other hydraulic elements, thereby protecting the oil pump and the system proportional pressure regulating valve 1.

[0062] In the hydraulic control system, the oil suction filter 13 can filter large particle impurities, but the filtering capacity for small particles is limited, therefore, the hydraulic control system is also provided with a high-pressure filter 17, the outlet end of the first pump body 2 is communicated to the inlet end of the high-pressure filter 17, and the outlet end of the high-pressure filter 17 is respectively communicated to the first port 103 and the third port 105 of the system proportional pressure regulating valve 1, the inlet end of the first electromagnetic valve 4, the inlet end of the second electromagnetic valve 5, the inlet end of the third electromagnetic valve 6 and the first pressure sensor 18.

[0063] The high-pressure filter 17 can effectively remove small particle impurities in the hydraulic oil, protect the hydraulic elements from wear, prolong the service life of the system, and ensure the reliable operation of the key components.

[0064] In the embodiments provided by the utility model, referring to Figure 2 As shown in the figure, the first pipeline 23 is sequentially provided with a one-way valve 14, an oil cooler 15 and a fine filter 16, the one-way valve 14 is used for controlling the hydraulic oil to flow in a predetermined direction and cannot flow reversely, the oil cooler 15 is used for reducing the temperature of the hydraulic oil to prevent the motor and the gear shaft system from being damaged due to high temperature, and the clean hydraulic oil after the fine filter 16 provides lubrication for the motor and the gear shaft system, reduces wear and prolongs the service life of the equipment.

[0065] The communication between the second pipeline 24 and the first pipeline 23 is located between the fine filter 16 and the P3 motor 9, the hydraulic oil is branched to the second pipeline 24 between the fine filter 16 and the P3 motor 9 to provide cooling and lubrication for the P1 motor 8, the hydraulic oil of the first pipeline 23 continues to flow to the P3 motor 9 to provide cooling and lubrication for the P3 motor 9, and the communication between the fourth port 106 of the system proportional pressure regulating valve 1 and the first pipeline 23 is located before the oil cooler 15, so that the system proportional pressure regulating valve 1 can adjust the pressure before the hydraulic oil enters the cooler, thereby optimizing the working efficiency of the hydraulic control system.

[0066] When the second pump body 3 starts, the hydraulic oil is sucked from the oil sump 12 through the oil suction filter 13, discharged through the second pump body 3, and then cooled and lubricated for the motor and the gear shaft system through the one-way valve 14, the oil cooler 15 and the fine filter 16, so that the hydraulic oil is cooled and finely filtered before entering the P3 motor 9 and the P1 motor 8, thereby providing clean and suitable temperature hydraulic oil to protect the motor and the gear shaft system.

[0067] In the hydraulic control system, especially when the clutch is switched or the electromagnetic valve is actuated, instantaneous hydraulic impact may be generated, therefore, referring to Figure 2As shown, the pipeline between the second electromagnetic valve 5 and the first clutch 10 is provided with a first accumulator 19 and a second pressure sensor 20. The pipeline between the third electromagnetic valve 6 and the second clutch 11 is provided with a second accumulator 21 and a third pressure sensor 22.

[0068] The first accumulator 19 and the second accumulator 21 can effectively absorb hydraulic impact, protect the elements in the system, and at the same time store hydraulic energy and release when needed, thereby maintaining the stability of the system pressure, reducing pressure fluctuations, and ensuring that the first clutch 10, the second clutch 11 or other key components complete the necessary actions. The second pressure sensor 20 and the third pressure sensor 22 are used to monitor the pressure of the hydraulic oil in the clutch pipeline, ensure that the system operates within a safe and efficient pressure range, and precisely control the engagement and disengagement of the first clutch 10 and the second clutch 11 to optimize shift quality.

[0069] Based on the hydraulic control system provided in the above embodiment, the working mode of the system proportional pressure regulating valve 1 is as follows:

[0070] When the engine is started and the clutch is not working, all electromagnetic valves are not powered, the hydraulic oil pumped out by the first pump body 2 enters the first chamber 112 through the first port 103 to generate a first force to the right of the valve core 108, at this time the valve core 108 only needs to overcome the elastic force of the elastic member 111, at this time the system pressure is small, the energy consumption is low, and the hydraulic oil supplied by the first pump body 2 is used to perform cooling and lubrication on the system. Safety strategy: 1. When the oil cooler 15 is blocked by impurities, or the pressure drop of the oil cooler 15 and the fine filter 16 is large due to extremely low temperature, the pressure at the rear end of the system proportional pressure regulating valve 1 is high, at this time the first force will increase to push the valve core 108 to continue to move to the right, at this time the valve core 108 is at the overlapping position of the first interval and the second interval, and the hydraulic oil enters the rear end from the third port 105, and then flows to the fourth port 106 through the first communication groove 109 and to the second port 104 through the second communication groove 110, thereby performing pressure limiting unloading to protect the oil cooler 15; 2. If the engine is started, and the system pressure is too high to exceed the set safety threshold due to the jamming of the system proportional pressure regulating valve 1 itself, the first pressure sensor 18 needs to perform fault alarm and force the engine to reduce speed or stop.

[0071] When the engine starts and the clutch works, the first electromagnetic valve 4 is powered on, and part of the hydraulic oil pumped by the first pump body 2 enters the fifth port 107 of the system proportional pressure regulating valve 1 through the first electromagnetic valve 4, providing the second force to the valve core 108, and the sum of the second force and the elastic force of the elastic member 111 forms a leftward resultant force, which, together with the first force formed by the main system pressure in the first chamber 112 of the system proportional pressure regulating valve 1, dynamically adjusts the opening size of the valve core 108 (the third port 105 to the fourth port 106 is connected but throttled) to generate a pressure drop, and when the forces on both ends reach dynamic balance, a stable value of the system pressure is obtained. The system pressure is collected by the first pressure sensor 18 and transmitted to the controller, and then the controller reads and analyzes the pressure signal and sends a control signal to the first electromagnetic valve 4 for control, forming a closed control system to accurately control the system pressure in real time. Safety strategy: 1. Before pressure regulating control, it is necessary to judge whether the system pressure without the participation of the first electromagnetic valve 4 exceeds the set safety threshold, if it is within the allowable range, the pressure regulating and clutch control can be carried out, otherwise the first electromagnetic valve 4 is not allowed to be powered on for pressure regulating; 2. If the engine is started, the system pressure P is too high to exceed the set safety threshold due to the self-stuck of the system proportional pressure regulating valve 1, the first pressure sensor 18 needs to issue a fault alarm and force the engine to slow down or stop.

[0072] When the engine does not start, the system proportional pressure regulating valve 1 and the first pressure sensor 18 do not work.

[0073] The above describes the structure, features and effects of the embodiments shown in the drawings, and the above is only a preferred embodiment of the present application, but the present application is not limited to the drawings shown, any change or modification made according to the concept of the present application, or equivalent embodiment with equivalent changes, as long as it does not exceed the spirit of the specification and drawings, should be within the protection scope of the present application.

Claims

1. A system proportional pressure regulating valve characterized by, The valve body is provided with a sliding groove, and a first port, a second port, a third port, a fourth port and a fifth port are sequentially arranged on the valve body along the extension direction of the sliding groove. A valve core is slidably arranged in the sliding groove, and a first communication groove and a second communication groove are sequentially arranged on the outer surface of the valve core along the axial direction of the valve core. An elastic member is arranged in the sliding groove and connected with the valve core to enable the valve core to elastically move back and forth in the sliding groove. The valve core has a first end and a second end, and a first chamber is formed between the first end face of the valve core and the inner surface of the sliding groove, and the first port is in communication with the first chamber. A first interval and a second interval are arranged on the moving path of the valve core, and the first interval and the second interval have a partially overlapped region. The end face area of the first end of the valve core is smaller than the end face area of the second end of the valve core. The elastic member comprises a spring arranged in the second chamber, and the opposite ends of the spring are respectively in abutment with the second end of the valve core and the inner wall surface of the sliding groove.

2. The system proportional pressure regulating valve of claim 1, wherein: The system proportional pressure regulating valve is the system proportional pressure regulating valve according to any one of claims 1 to 3, and the system proportional pressure regulating valve comprises a first pump body, a second pump body, a system proportional pressure regulating valve, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve and a first pressure sensor.

3. The system proportional pressure regulating valve of claim 1, wherein: The outlet end of the first pump body is in communication with the first port and the third port of the system proportional pressure regulating valve, the inlet end of the first electromagnetic valve, the inlet end of the second electromagnetic valve, the inlet end of the third electromagnetic valve and the first pressure sensor.

4. A hydraulic control system characterized by, The outlet end of the second pump body is in communication with a P3 motor through a first pipeline, and the first pipeline is in communication with a second pipeline. The fourth port of the system proportional pressure regulating valve is in communication with the second pipeline. The outlet end of the first electromagnetic valve is in communication with the fifth port of the system proportional pressure regulating valve. The outlet end of the second electromagnetic valve is in communication with a first clutch. The outlet end of the third electromagnetic valve is in communication with a second clutch. The first pump body is a mechanical pump, and the second pump body is an electronic oil pump. The first pump body is in communication with an oil pan through a third pipeline, and an oil suction filter is arranged on the third pipeline.

5. The hydraulic control system of claim 4, wherein: The second pump body is in communication with the third pipeline through a fourth pipeline, and the communication position of the fourth pipeline and the third pipeline is located between the oil suction filter and the first pump body.

6. The hydraulic control system of claim 4, wherein: ​ 7. The hydraulic control system of claim 4, wherein: The liquid outlet end of the first pump body is communicated to the liquid inlet end of a high-pressure filter, the liquid outlet end of the high-pressure filter is respectively communicated to the first port and the third port of the system proportional pressure regulating valve, the liquid inlet end of the first electromagnetic valve, the liquid inlet end of the second electromagnetic valve, the liquid inlet end of the third electromagnetic valve and the first pressure sensor.

8. The hydraulic control system of claim 4, wherein: A one-way valve, an oil cooler and a fine filter are sequentially arranged on the first pipeline, and the communication position of the second pipeline and the first pipeline is between the fine filter and the P3 motor.

9. The hydraulic control system of claim 4, wherein: A first accumulator and a second pressure sensor are arranged on the pipeline between the second electromagnetic valve and the first clutch.

10. The hydraulic control system of claim 4, wherein: A second accumulator and a third pressure sensor are arranged on the pipeline between the third electromagnetic valve and the second clutch.

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