WO2024139378A1

WO2024139378A1 - Hydraulic module of mechatronic coupling transmission and decoupling and coupling mode switching method

Info

Publication number: WO2024139378A1
Application number: PCT/CN2023/117315
Authority: WO
Inventors: 周家豪; 杨洋; 王川; 鲁宜国; 陈绍维
Original assignee: 广州汽车集团股份有限公司
Priority date: 2022-12-27
Filing date: 2023-09-06
Publication date: 2024-07-04

Abstract

A hydraulic module of a mechatronic coupling transmission, comprising a first valve plate (1), a second valve plate (2) and a middle partition plate (3); the first valve plate (1) and the second valve plate (2) are fixedly pressed onto two sides of the middle partition plate (3), so that an oil channel cast in the first valve plate (1) and an oil channel cast in the second valve plate (2) are both sealed. The first valve plate (1) is provided with a mechanical spool valve assembly which actuates frequently and a pressure accumulator assembly (100). The mechanical spool valve assembly comprises a decoupling valve assembly (110), the decoupling valve assembly (110) being used for performing decoupling and coupling control according to a preset overlap amount during dual-pump oil supply by an electronic pump and a mechanical pump. The pressure accumulator assembly (100) is used for reducing pressure fluctuation of a specific oil path. The second valve plate (2) is provided with a filter press assembly (200), the filter press assembly (200) being used for filtering oil in a high-pressure-control oil path. Also disclosed are a hybrid electric vehicle and a decoupling and coupling mode switching method.

Description

Hydraulic module of electromechanical coupling transmission and decoupling and coupling mode switching method

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to the Chinese patent application filed with the China Patent Office on December 27, 2022, with application number 202211689854.6, and patent application name "Hydraulic module of electromechanical coupling transmission and decoupling and coupling mode switching method", and the Chinese patent application filed with the China Patent Office on December 27, 2022, with application number 2022223549604.0, and patent application name "Hydraulic module of electromechanical coupling transmission and hybrid vehicle", all of which are incorporated by reference into this application.

Technical Field

The present application relates to the technical field of transmissions, and in particular to a hydraulic module of an electromechanical coupling transmission, a hybrid vehicle, and a method for switching between decoupling and coupling modes.

Background technique

At present, the filters used in the hydraulic modules of electromechanical coupling transmissions are basically mesh-type coarse filters, and the cleanliness safety factor is not high enough; at the same time, when the electronic pump and the mechanical pump are dual-pump oil supply, the hydraulic module does not have the decoupling and coupling functions, resulting in all oil being high-pressure oil, which will increase system energy consumption and reduce the transmission efficiency of the transmission; in terms of valve plate layout, frequently actuated mechanical sliding valves are arranged on the upper and lower valve plates, which leads to an increase in the cost of the anodizing process.

Summary of the invention

The main purpose of the embodiment of the present application is to provide a hydraulic module of an electromechanical coupling transmission, a hybrid vehicle, and a method for switching between decoupling and coupling modes. The purpose is to set a decoupling valve assembly and a filter press assembly in the hydraulic module, and the decoupling valve assembly can be used to switch between decoupling and coupling modes. The filter press assembly can ensure cleanliness and prevent the solenoid valve from getting stuck.

To achieve the above-mentioned purpose, a first aspect of an embodiment of the present application provides a hydraulic module of an electromechanical coupling transmission, comprising a first valve plate, a second valve plate and a middle partition plate;

The first valve plate and the second valve plate are fixedly pressed on both sides of the middle partition plate so that the oil passage cast on the first valve plate and the oil passage cast on the second valve plate are both sealed;

The first valve plate is provided with a frequently actuated mechanical sliding valve assembly and a pressure accumulator assembly;

The mechanical slide valve assembly includes a decoupling valve assembly, and the decoupling valve assembly is used to perform decoupling and coupling control according to a preset overlap amount when the electronic pump and the mechanical pump are dual pumping oil;

The accumulator assembly is used to reduce pressure fluctuations in a specific oil circuit;

The second valve plate is provided with a filter pressure assembly, and the filter pressure assembly is used to filter the oil in the high-pressure control oil circuit.

In some embodiments, the decoupling valve assembly includes a valve core, a spring, a plug and a baffle;

The valve core, the spring and the plug are fixed together in the first valve hole of the first valve plate through the baffle, and the spring is installed between the valve core and the plug;

The spring is compressed or extended according to the change of the hydraulic pressure applied to the end surface of the valve core, so that the valve core slides in the first valve hole;

The valve core is arranged at the first position of the first valve hole so that the default working state of the decoupling valve assembly is the coupling state. state;

When the speed of the mechanical pump reaches the control pressure requirement of the main oil circuit, the corresponding liquid pressure is provided to the valve core end face according to the preset overlap amount, so that the valve core moves from the first position of the first valve hole to the second position within the corresponding switching time, so that the working state of the decoupling valve assembly is switched to the decoupling state.

In some embodiments, the second valve plate is further provided with a switch solenoid valve assembly;

The switch solenoid valve assembly is fixed in the second valve hole of the second valve plate by means of a bayonet and a bolt, and is used to control the oil circuit outlet to be connected with the valve core end face of the decoupling valve assembly so as to adjust the liquid pressure of the valve core end face of the decoupling valve assembly.

In some embodiments, the filter press assembly includes a cover plate, a sealing gasket, and a filter element;

The filter element is installed in a filter element container provided on the second valve plate, the contact surface between the filter element and the inner wall of the filter element container is sealed, and the sealing gasket is installed between the upper surface of the filter element container and the cover plate to seal the filter element into the filter element container;

The outer cavity of the filter element is connected to the oil inlet, and the hollow inner cavity of the filter element is connected to the oil outlet, so that the oil flows in from the outer cavity of the filter element and flows out from the hollow inner cavity of the filter element;

The filter element has an integrated bypass valve in the center. When the pressure difference between the front and rear ends of the filter element is greater than the opening pressure of the bypass valve, the bypass valve opens to allow part of the oil to enter and flow out through the bypass valve.

In some embodiments, the mechanical sliding valve assembly further comprises a main pressure regulating valve assembly, and the structure of the main pressure regulating valve assembly is the same as that of the decoupling valve assembly;

The main pressure regulating valve assembly is fixed in the third valve hole of the first valve plate and is used for regulating the main oil pressure in the oil circuit.

In some embodiments, a pilot proportional solenoid valve assembly is further provided on the second valve plate;

The pilot proportional solenoid valve assembly is fixed in the fourth valve hole of the second valve plate by means of a bayonet and a bolt, and is used to control the oil circuit outlet to be connected with the valve core end face of the main pressure regulating valve assembly to adjust the liquid pressure on the valve core end face of the main pressure regulating valve assembly.

In some embodiments, the mechanical sliding valve assembly further includes a relief valve assembly, and the structure of the relief valve assembly is the same as that of the decoupling valve assembly;

The overflow valve assembly is fixed in the fifth valve hole of the first valve plate, and is used to overflow the oil back to the oil tank when the oil flow in the oil circuit is greater than a preset value.

In some embodiments, a cooling switching valve assembly is further provided on the second valve plate, and the structure of the cooling switching valve assembly is the same as that of the decoupling valve assembly;

The cooling switching valve assembly is fixed in the sixth valve hole of the second valve plate, and is used to cool and lubricate the corresponding working components by directing oil to the working components.

In some embodiments, a pressure limiting valve assembly is further provided on the second valve plate, and the structure of the pressure limiting valve assembly is the same as that of the decoupling valve assembly;

The pressure-limiting valve assembly is fixed in the seventh valve hole of the second valve plate, and is used to limit the maximum pressure of the main oil circuit.

In some embodiments, a clutch direct-drive solenoid valve assembly and a pressure sensor assembly are also provided on the second valve plate;

The clutch direct drive solenoid valve assembly is used to control the oil circuit outlet to communicate with the oil circuit at the clutch end to adjust the pressure at the clutch end;

The pressure sensor assembly is used to detect the pressure of a specific oil channel.

In some embodiments, the middle partition is provided with a throttling hole;

The throttle holes are used to distribute different cooling and lubrication flows to different oil circuits.

To achieve the above-mentioned purpose, a second aspect of an embodiment of the present application proposes a hybrid vehicle, comprising a hydraulic module of the electromechanical coupling transmission described in the first aspect.

To achieve the above-mentioned purpose, a third aspect of an embodiment of the present application proposes a method for switching decoupling and coupling modes of an electromechanical coupling transmission, which is implemented based on the hydraulic module described in the first aspect and includes:

When the electronic pump and the mechanical pump are both supplying oil, determine whether the speed of the mechanical pump meets the control pressure requirement of the main oil circuit;

If the mechanical pump speed does not meet the main oil circuit control pressure requirement, the decoupling valve assembly is controlled to be in a coupled state;

When the speed of the mechanical pump changes to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the coupling state to the decoupling state according to a preset overlap amount;

When the speed of the mechanical pump changes to a point where it fails to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the decoupling state back to the coupling state.

In some embodiments, determining whether the mechanical pump speed meets the main oil circuit control pressure requirement includes:

comparing the mechanical pump rotation speed with a first preset rotation speed;

If the speed of the mechanical pump does not exceed the first preset speed, it is determined that the speed of the mechanical pump does not meet the control pressure requirement of the main oil circuit;

If the rotation speed of the mechanical pump exceeds the first preset rotation speed, it is determined that the rotation speed of the mechanical pump meets the control pressure requirement of the main oil circuit.

In some embodiments, when the speed of the mechanical pump changes to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the coupled state to the decoupled state according to a preset overlap amount, including:

When the speed of the mechanical pump changes to exceed the first preset speed, it is determined that the speed of the mechanical pump meets the control pressure requirement of the main oil circuit;

Determining the hydraulic pressure and switching duration required to be provided to the valve core end face of the decoupling valve assembly according to the preset overlap amount;

The valve core of the decoupling valve assembly is controlled by the hydraulic pressure to move within the switching time period, so as to switch the decoupling valve assembly from the coupling state to the decoupling state.

The present application proposes a hydraulic module of an electromechanical coupling transmission, a hybrid vehicle and a decoupling and coupling mode switching method, wherein the hydraulic module includes a first valve plate, a second valve plate and an intermediate partition; the first valve plate and the second valve plate are fixedly pressed on both sides of the intermediate partition so that the oil passages cast on the first valve plate and the oil passages cast on the second valve plate are both sealed; a frequently actuated mechanical sliding valve assembly and an accumulator assembly are arranged on the first valve plate; the mechanical sliding valve assembly includes a decoupling valve assembly, which is used for decoupling and coupling control according to a preset overlap amount when the electronic pump and the mechanical pump are dual-pumped to supply oil; the accumulator assembly is used for reducing pressure fluctuations in a specific oil circuit; a filter press assembly is arranged on the second valve plate, which is used for filtering the oil in the high-pressure control oil circuit. The decoupling valve assembly can be used to switch between decoupling and coupling modes, thereby reducing energy consumption losses; the filter press assembly can ensure cleanliness and prevent the solenoid valve from getting stuck; the frequently actuated mechanical sliding valve assembly and accumulator assembly are centrally arranged on the first valve plate, so that only the first valve plate needs to be anodized, which can reduce wear and improve system reliability; at the same time, the hydraulic module has high integration, compact structure, light weight, and is easy to arrange and install.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is an overall structural diagram of a hydraulic module of an electromechanical coupling transmission provided in an embodiment of the present application;

FIG2 is a structural diagram of a first valve plate provided in an embodiment of the present application;

FIG3 is a structural diagram of a second valve plate provided in an embodiment of the present application;

FIG4 is a structural diagram of a decoupling valve assembly provided in an embodiment of the present application;

FIG5 is a schematic structural diagram of a filter press assembly provided in an embodiment of the present application;

FIG6 is a schematic diagram of a coupling state of a decoupling valve assembly provided in an embodiment of the present application;

FIG7 is a schematic diagram of a decoupling state of a decoupling valve assembly provided in an embodiment of the present application;

FIG8 is a schematic diagram of an overlapping state of a decoupling valve assembly provided in an embodiment of the present application;

9 is a flowchart of the steps of a method for switching decoupling and coupling modes of an electromechanical coupling transmission provided in an embodiment of the present application;

10 is a flowchart of the steps of determining whether the mechanical pump speed meets the main oil circuit control pressure requirement according to an embodiment of the present application;

11 is a flowchart of the steps provided in an embodiment of the present application for controlling the decoupling valve assembly to switch from a coupled state to a decoupled state according to a preset overlap amount when the mechanical pump speed changes to meet the main oil circuit control pressure requirement.

Detailed ways

In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

It should be noted that, although the functional modules are divided in the device schematic diagram and the logical order is shown in the flowchart, in some cases, the steps shown or described may be performed in a different order than the module division in the device or the order in the flowchart. The terms "first", "second", etc. in the specification, claims and the above drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence.

Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art to which this application belongs. The terms used herein are only for the purpose of describing the embodiments of this application and are not intended to limit this application.

Electromechanical coupling transmission involves the energy flow between the engine, drive motor and starting motor. It has many working modes and a high switching frequency between different modes. It has strict control requirements on the engagement and separation of the clutch and brake. At the same time, compared with traditional transmissions, electromechanical coupling transmissions also involve the heat dissipation of the generator and drive motor, and the cooling flow demand is large. Therefore, how to achieve accurate and efficient mode switching and reasonable cooling flow matching at the same time is particularly important in the design of hydraulic modules. Secondly, considering the fuel consumption, regulations, reliability and other issues of the whole vehicle, further reducing the energy consumption of the hydraulic system and improving the integration of the hydraulic module and product reliability are also key technologies in the development process of hydraulic modules.

At present, the filters used in the hydraulic control modules of electromechanical coupling transmissions are basically mesh-type coarse filters, and the cleanliness safety factor is not high enough; at the same time, no decoupling valve assembly is provided, and the decoupling and coupling functions are not available; in terms of valve plate arrangement, frequently actuated mechanical sliding valves are arranged on the upper and lower valve plates, resulting in the need for anodizing treatment of the upper and lower valve plates, which increases the cost of the anodizing process.

Based on this, an embodiment of the present application provides a hydraulic module of an electromechanical coupling transmission. By integrating a decoupling valve assembly and a filter press assembly in the hydraulic module, the decoupling and coupling mode switching can be achieved through the decoupling valve assembly, and the filter press assembly can ensure cleanliness and prevent the solenoid valve from getting stuck. Referring to Figures 1-3, Figure 1 is an overall structural diagram of the hydraulic module of the electromechanical coupling transmission provided in an embodiment of the present application; Figure 2 is a structural diagram of the first valve plate provided in an embodiment of the present application; and Figure 3 is a structural diagram of the second valve plate provided in an embodiment of the present application. The hydraulic module includes a first valve plate 1, a second valve plate 2, and a middle partition plate 3;

The first valve plate 1 and the second valve plate 2 are fixedly pressed on both sides of the middle partition plate 3, so that the oil passages cast on the first valve plate 1 and the oil passages cast on the second valve plate 2 are both sealed;

The first valve plate 1 is provided with a frequently actuated mechanical sliding valve assembly and a pressure accumulator assembly 100;

The mechanical slide valve assembly includes a decoupling valve assembly 110, which is used to perform decoupling and coupling control according to a preset overlap amount when the electronic pump and the mechanical pump are dual pumping oil;

The accumulator assembly 100 is used to reduce pressure fluctuations in a specific oil circuit;

A filter press assembly 200 is provided on the second valve plate 2, and the filter press assembly 200 is used to filter the oil in the high-pressure control oil circuit.

The middle partition plate 3 is provided with a throttling hole 301, and the throttling hole 301 is used to distribute different cooling and lubrication flows to different oil circuits.

In the embodiment of the present application, as shown in FIG. 2 , there are multiple accumulator assemblies 100 disposed on the first valve plate, and each accumulator assembly is used to reduce pressure fluctuations in the oil circuit in which the accumulator assembly is located.

In the embodiment of the present application, the first valve plate and the second valve plate are both cast with curved and staggered oil passages inside, which realize the corresponding fluid control function together with the different components installed on the respective valve plates. The first valve plate, the second valve plate and the middle partition are connected by bolts to tighten and ensure the sealing of each oil passage. In the embodiment of the present application, the mechanical sliding valve assembly and the accumulator assembly with frequent actuation are arranged on the first valve plate, so that only the first valve plate needs to be anodized, which can reduce wear and reduce the cost of the anodizing process. By arranging a decoupling valve assembly on the first valve plate, the decoupling valve assembly can be used to switch between decoupling and coupling modes, thereby reducing energy consumption losses. By arranging a filter press assembly on the second valve plate and filtering the oil in the high-pressure control oil circuit through a high-precision filter press assembly, the cleanliness can be ensured and the solenoid valve can be prevented from getting stuck.

2 , a plurality of accumulator assemblies 100 and frequently actuated mechanical slide valve assemblies are disposed on the first valve plate 1 . The frequently actuated mechanical slide valve assembly includes a decoupling valve assembly 110 , a main pressure regulating valve assembly 120 and a relief valve assembly 130 .

The accumulator assembly 100 is mounted on the first valve plate and fixed with a retaining spring, and the pressure fluctuation of the oil circuit is reduced through the energy absorption effect of the spring movement.

Referring to FIG. 4 , FIG. 4 is a structural diagram of a decoupling valve assembly provided in an embodiment of the present application; as shown in FIG. 4 , the decoupling valve assembly 110 includes a valve core 111 , a spring 112 , a plug 113 and a baffle 114 ;

The valve core 111, the spring 112 and the plug 113 are fixed together in the first valve hole of the first valve plate 1 through the baffle 114, and the spring 112 is installed between the valve core 111 and the plug 113;

The spring 112 is compressed or extended according to the change of the hydraulic pressure on the end surface of the valve core 111, so that the valve core 111 slides in the first valve hole;

The valve core 111 is arranged at a first position of the first valve hole, so that the default working state of the decoupling valve assembly 110 is a coupled state;

When the mechanical pump speed reaches the main oil circuit control pressure requirement, the corresponding liquid pressure is provided to the valve core end face according to the preset overlap amount, so that the valve core 111 moves from the first position of the first valve hole to the second position within the corresponding switching time, so that the working state of the decoupling valve assembly 110 is switched to the decoupling state.

The embodiment of the present application can achieve dual-pump high- and low-pressure decoupling and coupling mode switching through a decoupling valve assembly. The high- and low-pressure coupling ensures the normal function of the clutch and brake engagement. The high- and low-pressure decoupling greatly reduces the energy loss of the cooling front end and the power demand of the electronic pump, which helps to improve transmission efficiency and reduce costs.

The main pressure regulating valve assembly 120 has the same structure as the decoupling valve assembly 110 and is also composed of a valve core, a spring, a plug, and a baffle.

Specifically, the main pressure regulating valve assembly 120 is fixed in the third valve hole of the first valve plate 1 and is used to regulate the main oil pressure in the oil circuit.

The structure of the overflow valve assembly 130 is the same as that of the decoupling valve assembly 110 , and is also composed of a valve core, a spring, a plug, and a baffle.

Specifically, the overflow valve assembly 130 is fixed in the fifth valve hole of the first valve plate 1 and is used to open the overflow valve assembly 130 when the oil flow in the oil circuit is greater than When the preset value is reached, the oil overflows back to the tank.

3 , the second valve plate 2 is provided with a filter press assembly 200 , a switch solenoid valve assembly 210 , a pilot proportional solenoid valve assembly 220 , a cooling switching valve assembly 230 , a pressure limiting valve assembly 240 , a plurality of clutch direct drive solenoid valve assemblies 250 and a plurality of pressure sensor assemblies 260 .

Wherein, referring to Fig. 5, Fig. 5 is a schematic diagram of the structure of the filter press assembly provided in the embodiment of the present application. As shown in Fig. 5, the filter press assembly 200 includes a cover plate 201, a sealing gasket 202 and a filter element 203;

The filter element 203 is installed in the filter element container 270 provided on the second valve plate 2, the filter element 203 is sealed with the inner wall contact surface of the filter element container 270, and the sealing gasket 202 is installed between the upper surface of the filter element container 270 and the cover plate 201 to seal the filter element 203 into the filter element container 270;

The outer cavity of the filter element 203 is connected to the oil inlet, and the hollow inner cavity of the filter element 203 is connected to the oil outlet, so that the oil flows in from the outer cavity of the filter element 203 and flows out from the hollow inner cavity of the filter element 203;

A bypass valve is integrated in the center of the filter element 203. When the pressure difference between the front and rear ends of the filter element 203 is greater than the opening pressure of the bypass valve, the bypass valve opens to allow part of the oil to enter and flow out through the bypass valve; this can effectively reduce the flow resistance.

The embodiment of the present application can ensure high cleanliness, prevent the solenoid valve from getting stuck, and improve product reliability by setting a high-precision filter pressure assembly at the front end of the clutch direct-drive solenoid valve. The filter pressure assembly is installed on the hydraulic module body, which has high integration, compact structure, light weight, and is easy to arrange and install. At the same time, the bypass valve is integrated in the filter element of the filter pressure assembly, which has a compact structure and can reduce flow resistance loss to a certain extent and improve efficiency.

The switch solenoid valve assembly 210 is fixed in the second valve hole of the second valve plate 2 by means of a bayonet and a bolt, and is used to control the oil circuit outlet to be connected with the valve core end face of the decoupling valve assembly 110 to adjust the liquid pressure of the valve core end face of the decoupling valve assembly 110 .

The pilot proportional solenoid valve assembly 220 is fixed in the fourth valve hole of the second valve plate 2 by means of a bayonet and a bolt, and is used to control the oil circuit outlet to be connected with the valve core end face of the main pressure regulating valve assembly 120 to adjust the liquid pressure on the valve core end face of the main pressure regulating valve assembly 120.

The structure of the cooling switching valve assembly 230 is the same as that of the decoupling valve assembly 110, and is also composed of a valve core, a spring, a plug, and a baffle. The cooling switching valve assembly 230 is fixed in the sixth valve hole of the second valve plate 2, and is used to cool and lubricate the working parts by diverting oil to the corresponding working parts.

The structure of the pressure limiting valve assembly 240 is the same as that of the decoupling valve assembly 110, and is also composed of a valve core, a spring, a plug, and a baffle. The pressure limiting valve assembly 240 is fixed in the seventh valve hole of the second valve plate 2 to limit the maximum pressure of the main oil circuit.

There are multiple clutch direct drive solenoid valve assemblies 250, all of which are fixed in the corresponding valve holes of the second valve plate 2 through baffles and bolts, and are used to control the oil circuit outlet to communicate with the oil circuit at the clutch end, so as to adjust the pressure at the clutch end by using current signal proportional control;

There are multiple pressure sensor assemblies 260, all of which are installed in the second valve plate 2 through threads. The contact surface between the pressure sensor assembly 260 and the second valve plate 2 is sealed by an O-ring to detect the pressure of the oil channel.

It should be noted that the sealing method using a sealing gasket or an O-ring in the embodiment of the present application is merely illustrative of one of the sealing methods, and the embodiment of the present application does not specifically limit the sealing method.

In the embodiment of the present application, the working process of the hydraulic module shown in FIG1 is as follows:

The hydraulic module has two oil inlets, one for the low-pressure electronic oil pump and the other for the high-pressure mechanical oil pump. After the two streams of oil enter the hydraulic module, they are eventually distributed to the low-pressure cooling lubrication oil circuit and the high-pressure control oil circuit through the internal oil passages and various valve components. The low-pressure cooling lubrication oil circuit is responsible for the lubrication and cooling of the clutch, brake, bearing, gear and other parts in the electromechanical coupling gearbox to prevent abnormal wear or overheating and failure; the high-pressure control oil circuit is mainly responsible for the engagement and disengagement of the clutch and brake to achieve different vehicle driving modes.

The hydraulic module oil supply modes include electronic pump oil supply alone, mechanical pump oil supply alone, and electronic pump and mechanical pump oil supply together. Three situations of oil.

When the electronic pump supplies oil alone and the mechanical pump supplies oil alone, the oil enters the hydraulic module and flows to the front end of the main pressure regulating valve assembly, and then adjusts the current of the pilot proportional solenoid valve assembly to make the main oil pressure reach the required value. The clutch direct drive solenoid valve assembly is located in the main oil pressure oil circuit, and can control the engagement and disengagement of different clutches according to the working requirements of different modes of the whole machine. After passing through the main pressure regulating valve assembly, the oil flows to the cooling and lubricating oil circuit, and different cooling and lubricating flows are allocated to different oil circuits through the design of the throttle hole on the middle partition.

When the electronic pump and the mechanical pump supply oil together, there are two different modes according to the working state of the decoupling valve assembly. As shown in Figure 6, Figure 6 is a schematic diagram of the coupling state of the decoupling valve assembly provided in an embodiment of the present application. The decoupling valve assembly is in a coupled state when it is in a normal state. At this time, the oil flowing in from the electronic pump is gathered into the high-pressure control oil circuit through the decoupling valve assembly, and coupled with the mechanical pump to provide high pressure to ensure the stability of the clutch control oil pressure when the mechanical pump rotates at a low speed. At the same time, setting the normal working state of the decoupling valve assembly to the coupled state can also improve the self-protection ability of the electromechanical coupling system in the single pump failure mode, and can ensure the basic functions of the hydraulic module in the case of a single pump. As shown in Figure 7, Figure 7 is a schematic diagram of the decoupling state of the decoupling valve assembly provided in an embodiment of the present application. When the speed of the mechanical pump can meet the control pressure requirement of the main oil circuit, the switch solenoid valve assembly works to provide liquid pressure to the valve core end face of the decoupling valve assembly according to the preset overlap amount to control the decoupling valve assembly to switch to the decoupling state. At this time, the oil flowing in from the electronic pump directly flows into the cooling and lubrication oil circuit, which greatly reduces the load at the outlet end of the electronic pump, improves the system efficiency, reduces the power requirement of the electronic pump, and increases the service life of the electronic pump.

It should be noted that, as shown in FIG. 8 , FIG. 8 is a schematic diagram of the overlapping state of the decoupling valve assembly provided in an embodiment of the present application. During the switching process between the decoupling mode and the coupling mode of the decoupling valve assembly, it is not possible to directly switch from the coupling state to the decoupling state, but it is necessary to pass through an overlapping state in the middle. In order to ensure the oil pressure response characteristics of the low-pressure cooling lubrication oil circuit and the high-pressure control oil circuit, the embodiment of the present application can pre-design the overlap amount of a valve core according to experiments, so that the oil circuit is disconnected for a period of time during the switching process. The overlap amount is a key parameter in the design of the decoupling valve assembly.

Specifically, the meaning of the preset overlap is to apply a hydraulic pressure to the valve core end face of the decoupling valve assembly so as to control the valve core of the decoupling valve assembly to move from position A (coupled state) to position B (decoupling state) within a specific time period. The hydraulic pressure and the specific time period can be determined by the preset overlap. The overlapping state shown in Figure 8 is a state in which the decoupling valve assembly is located within a specific time period. The preset overlap can guide the design of the matching size of the decoupling valve core and the valve hole during the design process of the decoupling valve assembly, and the size of the hydraulic pressure that needs to be applied to the valve core end face of the decoupling valve can be obtained according to the preset overlap during the control switching process.

9 , which is a flow chart of the steps of a method for switching decoupling and coupling modes of an electromechanical coupling transmission provided in an embodiment of the present application, which is implemented based on the hydraulic module shown in FIG. 1 , including but not limited to steps S901 to S904 .

Step S901, when the electronic pump and the mechanical pump are both supplying oil, determine whether the speed of the mechanical pump meets the control pressure requirement of the main oil circuit;

Step S902, if the speed of the mechanical pump does not meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to be in a coupled state;

Step S903, when the speed of the mechanical pump changes to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the coupled state to the decoupled state according to the preset overlap amount;

Step S904: When the speed of the mechanical pump changes to a point where it fails to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the decoupling state back to the coupling state.

In the embodiment of the present application, as mentioned above, in the case of single pump oil supply, that is, when the electronic pump supplies oil alone and the mechanical pump supplies oil alone, it is not necessary to switch the decoupling and coupling modes through the decoupling valve assembly. When the electronic pump and the mechanical pump supply oil, it is determined whether the speed of the mechanical pump meets the control pressure requirement of the main oil circuit. Generally, when the vehicle is just started, the speed of the mechanical pump is higher than that of the main oil circuit. It is relatively low, and generally cannot meet the control pressure requirement of the main oil circuit. At this time, the decoupling valve assembly is controlled to be in a coupled state, that is, the decoupling valve assembly is controlled to maintain a normal working state. When the speed of the mechanical pump continues to increase to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the coupled state to the decoupling state according to the preset overlap amount. When the speed of the mechanical pump decreases to not meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the decoupling state back to the coupled state. Specifically, when the speed of the mechanical pump increases to exceed the first threshold, the decoupling valve assembly is controlled to switch from the coupled state to the decoupling state according to the preset overlap amount. When the speed of the mechanical pump gradually decreases to less than the second threshold, the decoupling valve assembly is controlled to switch from the decoupling state back to the coupled state. Among them, the second threshold is less than or equal to the first threshold.

It should be noted that when the control decoupling valve assembly is in the coupled state, the electronic pump is connected to the high-pressure control oil circuit to supply oil to the high-pressure control oil circuit and the low-pressure cooling lubricating oil circuit. When the control decoupling valve assembly is switched from the coupled state to the decoupled state, the electronic pump is connected to the low-pressure cooling lubricating oil circuit to supply oil to the low-pressure cooling lubricating oil circuit. In other words, when the control decoupling valve assembly is switched from the coupled state to the decoupled state, the electronic pump needs to be controlled to switch from being connected to the high-pressure control oil circuit to being connected to the low-pressure cooling lubricating oil circuit.

Referring to FIG. 10 , FIG. 10 is a flowchart of the steps for determining whether the mechanical pump speed meets the main oil circuit control pressure requirement provided in an embodiment of the present application, including but not limited to steps S1001 to S1003 .

Step S1001, comparing the mechanical pump speed with a first preset speed;

Step S1002, if the mechanical pump speed does not exceed the first preset speed, it is determined that the mechanical pump speed does not meet the main oil circuit control pressure requirement;

Step S1003: if the mechanical pump speed exceeds the first preset speed, it is determined that the mechanical pump speed meets the main oil circuit control pressure requirement.

In the embodiment of the present application, after the vehicle is started, the speed of the mechanical pump will gradually increase. At this time, the decoupling valve assembly maintains a normal working state, that is, a coupled state. When the speed of the mechanical pump increases to exceed the first preset speed, it can meet the main oil circuit control pressure requirement. At this time, it is necessary to control the decoupling valve assembly to switch from the coupled state to the decoupling state. If the mechanical pump has not increased to exceed the first preset speed, at this time, the speed of the mechanical pump cannot meet the main oil circuit control pressure requirement, and the decoupling valve assembly needs to be maintained in the coupled state.

Referring to Figure 11, Figure 11 is a flow chart of the steps provided in an embodiment of the present application for controlling the decoupling valve assembly to switch from a coupled state to a decoupled state according to a preset overlap amount when the mechanical pump speed changes to meet the main oil circuit control pressure requirement, including but not limited to steps S1101 to S1103.

Step S1101, when the speed of the mechanical pump changes to exceed the first preset speed, it is determined that the speed of the mechanical pump meets the control pressure requirement of the main oil circuit;

Step S1102, determining the hydraulic pressure and switching duration required to be provided to the valve core end face of the decoupling valve assembly according to the preset overlap amount;

Step S1103, controlling the valve core of the decoupling valve assembly to move within the switching time by hydraulic pressure, so as to switch the decoupling valve assembly from the coupled state to the decoupling state.

In an embodiment of the present application, when the speed of the mechanical pump changes to exceed the first preset speed, it is determined that the speed of the mechanical pump meets the control pressure requirement of the main oil circuit. At this time, the hydraulic pressure and switching time required to be provided to the valve core end face of the decoupling valve assembly are determined according to the preset overlap amount. Then, the valve core of the decoupling valve assembly is controlled by the hydraulic pressure to move within the switching time to switch the decoupling valve assembly from the coupled state to the decoupling state. For example, based on the preset overlap amount, it is determined that the hydraulic pressure required to be provided to the valve core end face of the decoupling valve assembly is P1 and the switching time is T1; at this time, the control switch solenoid valve assembly works to control the oil circuit outlet to be connected to the valve core end face of the decoupling valve assembly, thereby adjusting the hydraulic pressure on the valve core end face of the decoupling valve assembly to P1; under the action of the hydraulic pressure P1, the decoupling valve core will move in the first valve hole to switch the decoupling valve assembly from the coupled state to the decoupling state.

It should be noted that the hydraulic pressure P1 applied to the valve core end face of the decoupling valve assembly needs to satisfy the decoupling valve core movement time The device moves from position A (coupled state) to position B (decoupled state) within the switching time T1.

In the embodiment of the present application, the decoupling valve assembly can realize the high-low pressure decoupling and coupling mode switching of the dual pumps. The high-low pressure coupling ensures the normal function of the clutch and brake. The high-low pressure decoupling greatly reduces the energy loss of the cooling front end and the power demand of the electronic pump, which helps to improve the efficiency of the transmission and reduce costs. By controlling the decoupling and coupling mode switching by presetting the overlap amount, the oil pressure response timeliness of the high-pressure control oil circuit and the low-pressure cooling lubrication oil circuit can be guaranteed.

An embodiment of the present application also provides a hybrid vehicle, including the hydraulic module shown in Figures 1 to 3.

The embodiments described in the embodiments of the present application are intended to more clearly illustrate the technical solutions of the embodiments of the present application and do not constitute a limitation on the technical solutions provided in the embodiments of the present application. Those skilled in the art will appreciate that with the evolution of technology and the emergence of new application scenarios, the technical solutions provided in the embodiments of the present application are also applicable to similar technical problems.

Those skilled in the art will appreciate that the technical solutions shown in the figures do not constitute a limitation on the embodiments of the present application, and may include more or fewer steps than shown in the figures, or a combination of certain steps, or different steps.

The device embodiments described above are merely illustrative, and the units described as separate components may or may not be physically separated, that is, they may be located in one place, or they may be distributed on multiple network units. Some or all of the modules may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

Those skilled in the art will appreciate that all or some of the steps in the methods disclosed above, and the functional modules/units in the systems and devices may be implemented as software, firmware, hardware, or a suitable combination thereof.

The terms "first", "second", "third", "fourth", etc. (if any) in the specification of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchangeable where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any of their variations are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device comprising a series of steps or units is not necessarily limited to those steps or units clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

It should be understood that in the present application, "at least one (item)" means one or more, and "plurality" means two or more. "And/or" is used to describe the association relationship of associated objects, indicating that three relationships may exist. For example, "A and/or B" can mean: only A exists, only B exists, and A and B exist at the same time, where A and B can be singular or plural. The character "/" generally indicates that the objects associated before and after are in an "or" relationship. "At least one of the following" or similar expressions refers to any combination of these items, including any combination of single or plural items. For example, at least one of a, b or c can mean: a, b, c, "a and b", "a and c", "b and c", or "a and b and c", where a, b, c can be single or multiple.

In the several embodiments provided in the present application, it should be understood that the disclosed devices and methods can be implemented in other ways. For example, the device embodiments described above are only schematic. For example, the division of the above units is only a logical function division. There may be other division methods in actual implementation, such as multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the mutual coupling or direct coupling or communication connection shown or discussed can be through some interfaces, indirect coupling or communication connection of devices or units, which can be electrical, mechanical or other forms.

The units described above as separate components may or may not be physically separated, and the components shown as units may or may not be physical units, that is, they may be located in one place or distributed on multiple network units. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

The preferred embodiments of the present application are described above with reference to the accompanying drawings, but the scope of the rights of the present application is not limited thereto. Any modification, equivalent substitution and improvement made by a person skilled in the art without departing from the scope and essence of the present application should be within the scope of the rights of the present application.

Claims

A hydraulic module of an electromechanical coupling transmission, characterized in that it comprises a first valve plate, a second valve plate and a middle partition plate;

The first valve plate and the second valve plate are fixedly pressed on both sides of the middle partition plate so that the oil passage cast on the first valve plate and the oil passage cast on the second valve plate are both sealed;

The first valve plate is provided with a frequently actuated mechanical sliding valve assembly and a pressure accumulator assembly;

The mechanical slide valve assembly includes a decoupling valve assembly, and the decoupling valve assembly is used to perform decoupling and coupling control according to a preset overlap amount when the electronic pump and the mechanical pump are dual pumping oil;

The accumulator assembly is used to reduce pressure fluctuations in a specific oil circuit;

The second valve plate is provided with a filter pressure assembly, and the filter pressure assembly is used to filter the oil in the high-pressure control oil circuit.
The hydraulic module according to claim 1, characterized in that the decoupling valve assembly comprises a valve core, a spring, a plug and a baffle;

The valve core, the spring and the plug are fixed together in the first valve hole of the first valve plate through the baffle, and the spring is installed between the valve core and the plug;

The spring is compressed or extended according to the change of the hydraulic pressure applied to the end surface of the valve core, so that the valve core slides in the first valve hole;

The valve core is arranged at a first position of the first valve hole so that the default working state of the decoupling valve assembly is a coupled state;

When the speed of the mechanical pump reaches the control pressure requirement of the main oil circuit, the corresponding liquid pressure is provided to the valve core end face according to the preset overlap amount, so that the valve core moves from the first position of the first valve hole to the second position within the corresponding switching time, so that the working state of the decoupling valve assembly is switched to the decoupling state.
The hydraulic module according to claim 2, characterized in that the second valve plate is further provided with a switch solenoid valve assembly;

The switch solenoid valve assembly is fixed in the second valve hole of the second valve plate by means of a bayonet and a bolt, and is used to control the oil circuit outlet to be connected with the valve core end face of the decoupling valve assembly so as to adjust the liquid pressure of the valve core end face of the decoupling valve assembly.
The hydraulic module according to claim 1, characterized in that the filter press assembly comprises a cover plate, a sealing gasket and a filter element;

The filter element is installed in a filter element container provided on the second valve plate, the contact surface between the filter element and the inner wall of the filter element container is sealed, and the sealing gasket is installed between the upper surface of the filter element container and the cover plate to seal the filter element into the filter element container;

The outer cavity of the filter element is connected to the oil inlet, and the hollow inner cavity of the filter element is connected to the oil outlet, so that the oil flows in from the outer cavity of the filter element and flows out from the hollow inner cavity of the filter element;

The filter element has an integrated bypass valve in the center. When the pressure difference between the front and rear ends of the filter element is greater than the opening pressure of the bypass valve, the bypass valve opens to allow part of the oil to enter and flow out through the bypass valve.
The hydraulic module according to claim 1, characterized in that the mechanical sliding valve assembly further comprises a main pressure regulating valve assembly, and the structure of the main pressure regulating valve assembly is the same as that of the decoupling valve assembly;

The main pressure regulating valve assembly is fixed in the third valve hole of the first valve plate and is used for regulating the main oil pressure in the oil circuit.
The hydraulic module according to claim 5 is characterized in that a pilot proportional solenoid valve assembly is also provided on the second valve plate;

The pilot proportional solenoid valve assembly is fixed in the fourth valve hole of the second valve plate by means of a bayonet and a bolt, and is used to control The oil circuit outlet is communicated with the valve core end surface of the main pressure regulating valve assembly to adjust the hydraulic pressure of the valve core end surface of the main pressure regulating valve assembly.
The hydraulic module according to claim 1, characterized in that the mechanical slide valve assembly further comprises a relief valve assembly, and the structure of the relief valve assembly is the same as that of the decoupling valve assembly;

The overflow valve assembly is fixed in the fifth valve hole of the first valve plate, and is used to overflow the oil back to the oil tank when the oil flow in the oil circuit is greater than a preset value.
The hydraulic module according to claim 1, characterized in that a cooling switching valve assembly is further provided on the second valve plate, and the structure of the cooling switching valve assembly is the same as that of the decoupling valve assembly;

The cooling switching valve assembly is fixed in the sixth valve hole of the second valve plate, and is used to cool and lubricate the corresponding working components by directing oil to the working components.
The hydraulic module according to claim 1 is characterized in that a pressure limiting valve assembly is further provided on the second valve plate, and the structure of the pressure limiting valve assembly is the same as that of the decoupling valve assembly;

The pressure-limiting valve assembly is fixed in the seventh valve hole of the second valve plate, and is used to limit the maximum pressure of the main oil circuit.
The hydraulic module according to claim 1 is characterized in that a clutch direct drive solenoid valve assembly and a pressure sensor assembly are also provided on the second valve plate;

The clutch direct drive solenoid valve assembly is used to control the oil circuit outlet to communicate with the oil circuit at the clutch end to adjust the pressure at the clutch end;

The pressure sensor assembly is used to detect the pressure of a specific oil channel.
The hydraulic module according to claim 1, characterized in that the middle partition is provided with a throttling hole;

The throttle holes are used to distribute different cooling and lubrication flows to different oil circuits.
A hybrid electric vehicle, characterized by comprising a hydraulic module of the electromechanical coupling transmission according to any one of claims 1 to 11.
A method for switching decoupling and coupling modes of an electromechanical coupling transmission is implemented based on the hydraulic module according to any one of claims 1 to 11, and is characterized by comprising:

When the electronic pump and the mechanical pump are both supplying oil, determine whether the speed of the mechanical pump meets the control pressure requirement of the main oil circuit;

If the mechanical pump speed does not meet the main oil circuit control pressure requirement, the decoupling valve assembly is controlled to be in a coupled state;

When the speed of the mechanical pump changes to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the coupling state to the decoupling state according to a preset overlap amount;

When the speed of the mechanical pump changes to a point where it fails to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the decoupling state back to the coupling state.
The method according to claim 13 is characterized in that the step of judging whether the mechanical pump speed meets the main oil circuit control pressure requirement comprises:

comparing the mechanical pump rotation speed with a first preset rotation speed;

If the speed of the mechanical pump does not exceed the first preset speed, it is determined that the speed of the mechanical pump does not meet the control pressure requirement of the main oil circuit;

If the rotation speed of the mechanical pump exceeds the first preset rotation speed, it is determined that the rotation speed of the mechanical pump meets the control pressure requirement of the main oil circuit.
The method according to claim 14 is characterized in that when the speed of the mechanical pump changes to meet the control pressure requirement of the main oil circuit, the decoupling valve assembly is controlled to switch from the coupled state to the decoupled state according to a preset overlap amount, include:

When the speed of the mechanical pump changes to exceed the first preset speed, it is determined that the speed of the mechanical pump meets the control pressure requirement of the main oil circuit;

Determining the hydraulic pressure and switching duration required to be provided to the valve core end face of the decoupling valve assembly according to the preset overlap amount;

The valve core of the decoupling valve assembly is controlled by the hydraulic pressure to move within the switching time period, so as to switch the decoupling valve assembly from the coupling state to the decoupling state.