CN115076351A - Hydraulic control system - Google Patents

Abstract

The invention belongs to the technical field of transmissions and discloses a hydraulic control system which comprises a low-pressure lubricating circuit and a high-pressure lubricating oil circuit, wherein the low-pressure lubricating oil circuit comprises an oil groove, an electronic pump, a throttling hole group, a flow distribution slide valve, a generator cooling slide valve and a low-pressure oil circuit; the high-pressure lubrication line comprises an oil tank, a double-acting vane pump, a vane pump state switching slide valve, a vane pump check valve, a main oil pressure adjusting slide valve and a clutch pressure control electromagnetic valve, wherein the oil tank, the double-acting vane pump and the vane pump state switching slide valve are sequentially connected in series, oil is sequentially connected to the low-pressure oil circuit after passing through a first output port of the vane pump state switching slide valve and a vane pump check valve, and the second output port of the vane pump state switching slide valve is connected with the main oil pressure adjusting slide valve and the clutch pressure control electromagnetic valve in parallel, and the oil overflowing from the main oil pressure adjusting slide valve flows to the low-pressure oil circuit after passing through the vane pump check valve. The total flow demand can be reduced, the volumes of the electric pump and the mechanical pump are reduced, and the arrangement is convenient.

Description

Hydraulic control system

technical field

The present invention relates to the technical field of transmissions, and in particular, to a hydraulic control system.

Background technique

At present, under the background of the energy and environmental crisis, all car companies are vigorously promoting the research and development of new energy vehicles. Traditional fuel vehicles are highly dependent on energy, and have reached the limit of efficiency through long-term technological progress. It is difficult to further reduce fuel consumption and energy consumption through technological innovation. Electric vehicles have the advantages of zero emission and low noise, but the charging facilities are not perfect. , Low-temperature cruising range shrinks, and the pain point of high price is difficult to solve in the short term. Hybrid models supply the motor to drive the vehicle after the engine generates electricity in the best efficiency area at low speed. Vehicles have low fuel consumption, low noise, and cost the same as fuel vehicles. Therefore, the emergence of hybrid electric vehicles (HEV) has become the best solution before fully transitioning to pure electric vehicles.

At present, the common hybrid configurations on the market include Toyota's power split THS, series-parallel ones such as Honda i-MMD, BYD DM-i, and series-connected Nissan E-Power, etc. From the perspective of both power and economy, The series-parallel scheme has become the mainstream scheme in China.

In the existing hybrid vehicles, the oil source system of the hydraulic control device of the multi-speed hybrid transmission generally adopts two schemes. The scheme I adopts two mechanical pumps, one is a high-pressure pump driven by the engine, and the other is driven by the driving motor. Low-pressure pumps, which are coupled together to complete the required functions; scheme II is to use two separate electric pumps or an electric double oil pump, one is a low-pressure pump, mainly for cooling and lubrication, and the other is a high-pressure pump with an accumulator, which is executed on demand , the overall efficiency is higher.

However, in scheme I, the mechanical pump must meet the requirements of all working conditions, and the displacement is usually relatively large, because its speed depends on the speed of the engine and the speed of the drive motor, and cannot be actively adjusted, and the high-pressure pump only needs a large flow when shifting gears. In other working conditions, only a small flow rate is required to maintain the pressure, so there is energy waste in most working conditions.

Scheme II adopts the scheme of two electric pumps, the cost is very high, the space is large, and the cleanliness of the valve body and the sealing requirements are high. Moreover, the cooling and lubrication of each component in the two schemes is simply distributed through a fixed orifice or a flow distribution valve, and the cooling flow cannot be accurately distributed according to the hybrid working condition.

SUMMARY OF THE INVENTION

The purpose of the present invention is to provide a hydraulic control system, which can reduce the requirement of total flow, realize energy saving, and at the same time, can reduce the volume of the electric pump and the mechanical pump, and is convenient for arrangement.

For this purpose, the present invention adopts the following technical solutions:

A hydraulic control system comprising:

Low-pressure lubrication circuit: oil tank, electronic pump, orifice group, flow distribution slide valve, generator cooling slide valve and low-pressure oil circuit, the oil tank, the electronic pump and the low-pressure oil circuit are connected in series in sequence, and the throttle The hole group, the flow distribution slide valve, and the generator cooling slide valve are connected in parallel with the low-pressure oil circuit;

High-pressure lubrication circuit: the oil sump, double-acting vane pump, vane pump state switching spool valve, vane pump check valve, main oil pressure regulating spool valve and clutch pressure control solenoid valve, the oil sump, the double-acting vane pump, The vane pump state switching slide valves are connected in series in sequence, and the oil passes through the first output port of the vane pump state switching slide valve and the vane pump check valve and is connected to the low-pressure oil circuit, and the vane pump state The second output port of the switching spool valve is connected in parallel with the main oil pressure regulating spool valve and the clutch pressure control solenoid valve, and the oil overflowing from the main oil pressure regulating spool valve flows through the vane pump check valve to the Describe the low pressure oil circuit.

Preferably, an electronic pump check valve, a cooler and a filter press are arranged in sequence between the electronic pump and the low-pressure oil circuit, and the oil is connected to the electronic pump after passing through the vane pump check valve. between the check valve and the cooler.

Preferably, both ends of the valve core of the generator cooling spool valve are respectively connected to the front and rear oil passages of the main oil pressure regulating spool valve.

Preferably, a pilot solenoid valve is further included, and the pilot solenoid valve performs cooperative control on the positions of the vane pump state switching spool valve and the flow distribution spool valve.

Preferably, the pilot solenoid valve communicates with the second output port.

Preferably, it also includes a main oil pressure regulation pilot solenoid valve, the main oil pressure regulation pilot solenoid valve, the main oil pressure regulation spool valve, the pilot solenoid valve and the clutch pressure control solenoid valve are connected in parallel to the first Two output ports.

Preferably, the orifice group communicates with the shaft teeth, the bearing, the engine and the clutch.

Advantageously, the flow distribution spool valve communicates with the drive motor and the clutch.

The beneficial effects of the present invention: an electronic pump and a double-acting vane pump are used as the hydraulic power source, in the EV mode, the electric pump provides the flow of cooling and lubrication, and in the series and parallel modes, the electronic pump and the double-acting vane pump jointly provide cooling Lubrication flow and high pressure flow for clutch torque transmission or gear shifting. The two output ports of the double-acting vane pump are connected with a vane pump state switching spool valve. By switching the position of the spool valve, the two output ports can be merged and separated, and the oil pump displacement of the high-pressure oil circuit is adjusted according to the working conditions. High pressure and large flow are used for gear shifting, and high pressure and small flow are used to maintain pressure during driving to achieve energy saving. The flow of the low-pressure oil circuit is adjusted by two slide valves, which realizes accurate flow distribution according to different working conditions and cooling on demand, so it can reduce the demand for total flow, realize energy saving, and reduce the number of electric pumps and mechanical pumps. volume for easy layout.

Description of drawings

1 is a schematic diagram of a hydraulic control system provided by this embodiment;

FIG. 2 is a schematic diagram of the hydraulic control system provided by the present embodiment in a purely electric driving mode;

3 is a schematic diagram of the hydraulic control system provided in the present embodiment in a series mode;

FIG. 4 is a schematic diagram of the hydraulic control system provided in this embodiment in a direct drive mode;

FIG. 5 is a schematic diagram of the hydraulic control system provided in this embodiment in a shifting mode.

Detailed ways

The present invention will be 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 invention, but not to limit the present invention. In addition, it should be noted that, for the convenience of description, the drawings only show some but not all structures related to the present invention.

In the description of the present invention, unless otherwise expressly specified and limited, the terms "connected", "connected" and "fixed" should be understood in a broad sense, for example, it may be a fixed connection, a detachable connection, or an integrated ; It can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the internal connection of two elements or the interaction relationship between the two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood in specific situations.

In the present invention, unless otherwise expressly specified and limited, a first feature "on" or "under" a second feature may include the first and second features in direct contact, or may include the first and second features Not directly but through additional features between them. Also, the first feature being "above", "over" and "above" the second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is level higher than the second feature. The first feature is "below", "below" and "below" the second feature includes the first feature being directly below and diagonally below the second feature, or simply means that the first feature has a lower level than the second feature.

In the description of this embodiment, the terms "upper", "lower", "right", etc. are based on the orientation or positional relationship shown in the accompanying drawings, which are only for convenience of description and simplified operation, rather than indicating Or imply that the device or element referred to must have a particular orientation, be constructed and operate in a particular orientation, and therefore should not be construed as limiting the invention. In addition, the terms "first" and "second" are only used for distinction in description, and have no special meaning.

The present invention provides a hydraulic control system, as shown in FIG. 1 , the system includes a low-pressure lubrication line and a high-pressure lubrication line.

The low-pressure lubrication line includes oil tank 1, first suction filter 2A, electronic pump 3, vane pump check valve 6, electronic pump check valve 7, cooler 8, filter press 9, orifice group 10, flow distribution slide valve 11 , Generator cooling slide valve 12 .

The high-pressure lubrication line includes oil tank 1, second suction filter 2B, double-acting vane pump 4 (driven by the engine), vane pump state switching spool valve 5, main oil pressure regulating pilot solenoid valve 21, main oil pressure regulating spool valve 22, high pressure Oil circuit relief valve 23 , pilot solenoid valve 24 , first clutch pressure control solenoid valve 25 and second clutch pressure control solenoid valve 26 .

In the low-pressure lubrication circuit, after the electronic pump 3 is running, the oil in the oil tank 1 is drawn by the electronic pump 3 through the first suction filter 2A, and then passes through the check valve 7, the cooler 8, and the pressure filter 9 to the low-pressure oil circuit 13, and then is divided into three parts. Path: The first path is basically distributed to the shaft teeth, bearings, power motor P1, clutch C1 and clutch C2 through the throttle hole group 10; and the clutch C2 for cooling, and the third way cools the power motor P1 by adjusting the generator cooling spool valve 12 .

In the high-pressure lubrication circuit, if the engine is working and in the series power generation mode, the two output ports of the double-acting vane pump 4 both output low-pressure oil, the vane pump state switching slide valve 5 is in the initial position, and the first output port 16 of the vane pump discharges The oil discharged from the second output port 17 flows through the vane pump state switching slide valve 5 and the vane pump check valve 6 into the low pressure oil circuit 13, and the oil discharged from the second output port 17 passes through the vane pump state switching slide valve 5, the main oil pressure regulating slide valve 22, The vane pump check valve 6 also merges into the low-pressure oil circuit 13, and at this time, according to the cooling flow requirement of the hybrid system, the electronic pump 3 supplements the insufficient flow. If the engine works and is in the parallel direct drive mode, the second output port 17 of the double-acting vane pump 4 outputs high-pressure oil, and the first output port 16 outputs according to the working conditions: specifically, when the working condition 1 is running normally (clutch is pressed), Adjust the pressure of the pilot solenoid valve 24 so that the vane pump state switching spool valve 5 is in the initial position, the flow distribution spool valve 11 is in the second working position (from left to right), the first output port 16 outputs low-pressure oil, and the main oil pressure After the oil overflowing from the regulating slide valve 22 is combined, it flows into the low-pressure oil circuit 13 through the vane pump check valve 6 to cool and lubricate the components. Only the high-pressure oil of the second output port 17 can meet the system's high-pressure flow requirements; Condition 2 During power downshift or upshift, adjust the pressure of the pilot solenoid valve 24 so that the vane pump state switching spool valve 5 is in the working position (right position), and the flow distribution spool valve 11 is in the third or fourth working position (position three or four). Depending on the power downshift or upshift), the first output port 16 and the second output port 17 both output high-pressure oil after the confluence, to meet the large flow demand during shifting, and the low-pressure oil that overflows through the main oil pressure regulating spool valve 22 It flows into the low-pressure oil passage 13 through the vane pump check valve 6 to cool and lubricate the components, and the electronic pump 3 supplements the insufficient flow. Therefore, it is set that the first pressure of the vane pump state switching slide valve 5 to switch from the initial position to the working position is the same as the second pressure of the flow distribution slide valve 11 to switch to the third working position, that is, when the power is downshifted or upshifted, it is necessary to At the same time, the clutch C1 or clutch C2 also needs a large cooling flow. At this time, by adjusting the pilot solenoid valve 24, the coordinated control of the flow distribution spool valve 11 and the vane pump state switching spool valve 5 can be realized to meet the requirements of gear shifting. High and low pressure flow requirements.

The flow distribution of the entire system is achieved through the throttle orifice group 10 , the flow distribution slide valve 11 , the generator cooling slide valve 12 and the pilot solenoid valve 24 . The orifice group 10 distributes the flow to the bearing, shaft tooth, engine P3, clutch C1 and clutch C2, and then adjusts the pilot solenoid valve 24 to realize the switching of the four states of the flow distribution spool valve 11, and the engine can be realized according to the working conditions. P3, adjustment of flow distribution of clutch C1 and clutch C2.

The two ends of the valve core of the generator cooling spool valve 12 are respectively connected to the front and rear oil circuits of the main oil pressure regulating spool valve 22. When the hybrid transmission is in the series mode, the two output ports of the double-acting vane pump 4 both output low-pressure oil. Therefore, The oil pressure at both ends of the spool is the same, and the area on the left side of the spool is set to be larger than the area on the right side. At this time, the spool is switched to the working position, and the oil in the low-pressure oil circuit 13 cools the power motor P1 all the way; when the hybrid transmission is in parallel In mode, the double-acting vane pump 4 will output high pressure oil, the oil pressure on the right side of the spool is much greater than that on the left side, the spool is kept at the initial position, and no cooling oil is distributed to the power motor P1. The double-acting vane pump 4 does not run, there is no oil pressure at both ends of the spool of the generator cooling spool valve 12, the spool of the generator cooling spool valve 12 is kept at the initial position under the action of the spring, and no cooling oil is distributed to the power motor P1. Through this distribution system, accurate flow distribution and on-demand energy supply can be performed according to the working conditions of the hybrid transmission, and efficient cooling can be achieved.

Working condition 1: pure electric driving

The circuit relationship is shown in Figure 2. The power motor P1 drives the vehicle, and the cooling lubricating oil is provided by the electronic pump 3. The shaft teeth, bearings, transmission C1, and transmission C2 only provide basic cooling flow, and most of the flow is provided to the power motor P1 and then The drive motor P1 is cooled, and the electronic pump 3 is supplied as needed.

Case 2: Series Mode

The circuit relationship is shown in Figure 3. The engine drives the generator P3 to generate electricity, and the drive motor P1 drives the vehicle to drive. At this time, the cooling lubricating oil is mainly provided by the double-acting vane pump 4, with high efficiency. The insufficient part is supplemented by the electronic pump 3, and the shaft teeth , bearings, transmission C1 and transmission C2 only provide basic cooling flow, and most of the other flow is provided to power motor P1 and engine P3 for cooling.

Condition 3: Direct Drive Mode

The circuit relationship is shown in Figure 4. The engine directly drives the vehicle, and the excess power is generated by the drive motor P1. At this time, the cooling lubricating oil is mainly provided by the double-acting vane pump 4, with high efficiency, and the insufficient part is supplemented by the electronic pump 3. Shaft teeth, bearings, and drive motor P1 only provide basic cooling flow, engine P3 does not provide cooling oil, and most of the other flows are provided to transmission C1 and transmission C2 for cooling. The high-pressure oil is provided by the second output port 17 of the double-acting vane pump 4, and only maintains the lowest high-pressure flow of the system.

Condition 4: Shift Mode

The circuit relationship is shown in Figure 5. The engine directly drives the vehicle, and the excess power is generated by the drive motor P1. At this time, the cooling lubricating oil is mainly provided by the double-acting vane pump 4, with high efficiency, and the insufficient part is supplemented by the electronic pump 3. Shaft teeth, bearings, and drive motor P1 only provide basic cooling flow, while engine P3 does not supply cooling oil. When power downshifts and upshifts are to be performed, transmission C1 or transmission C2 requires a larger cooling flow during gear shifting. The distribution spool 11 is adjusted to position three or four and most of the flow is supplied to either transmission C1 or transmission C2 for cooling. The high-pressure oil is jointly provided by the first output port 16 and the second output port 17 of the double-acting vane pump 4, and outputs a large flow of high-pressure oil to meet the shifting requirements.

Obviously, the above-mentioned embodiments of the present invention are only examples for clearly illustrating the present invention, rather than limiting the embodiments of the present invention. For those of ordinary skill in the art, various obvious changes, readjustments and substitutions can be made without departing from the protection scope of the present invention. There is no need and cannot be exhaustive of all implementations here. Any modifications, equivalent replacements and improvements made within the spirit and principle of the present invention shall be included within the protection scope of the claims of the present invention.

Claims (8)

1. A hydraulic control system, comprising:

low-pressure lubrication line: the device comprises an oil groove (1), an electronic pump (3), a throttling hole group (10), a flow distribution slide valve (11), a generator cooling slide valve (12) and a low-pressure oil way (13), wherein the oil groove (1), the electronic pump (3) and the low-pressure oil way (13) are sequentially connected in series, and the throttling hole group (10), the flow distribution slide valve (11) and the generator cooling slide valve (12) are connected in parallel with the low-pressure oil way (13);

high-pressure lubrication line: oil groove (1), two effect vane pump (4), vane pump state switch slide valve (5), vane pump check valve (6), main oil pressure regulating slide valve (22) and clutch pressure control solenoid valve, oil groove (1) two effect vane pump (4) vane pump state switch slide valve (5) establish ties in proper order, and fluid passes through in proper order first delivery outlet (16) of vane pump state switch slide valve (5) with be connected to behind vane pump check valve (6) low pressure oil circuit (13), second delivery outlet (17) of vane pump state switch slide valve (5) are parallelly connected main oil pressure regulating slide valve (22) and clutch pressure control solenoid valve follow the fluid process of main oil pressure regulating slide valve (22) overflow flow extremely behind vane pump check valve (6) low pressure oil circuit (13).

2. The hydraulic control system according to claim 1, wherein an electronic pump check valve (7), a cooler (8) and a filter press (9) are further arranged between the electronic pump (3) and the low-pressure oil passage (13) in sequence, and the oil passes through the vane pump check valve (6) and then is connected between the electronic pump check valve (7) and the cooler (8).

3. The hydraulic control system according to claim 1, wherein both ends of a spool of the generator cooling spool (12) are connected to front and rear oil passages of the main oil pressure regulating spool (22), respectively.

4. The hydraulic control system according to claim 1, characterized by further comprising a pilot solenoid valve (24), the pilot solenoid valve (24) cooperatively controlling the positions of the vane pump state switching spool (5) and the flow distributing spool (11).

5. A hydraulic control system according to claim 4, characterized in that the pilot solenoid valve (24) and the second output port (17) communicate.

6. The hydraulic control system according to claim 5, characterized by further comprising a main oil pressure adjusting pilot solenoid valve (21), the main oil pressure adjusting spool (22), the pilot solenoid valve (24), and the clutch pressure control solenoid valve being connected in parallel to the second output port (17).

7. The hydraulic control system of claim 1, wherein the set of orifices (10) are connected to a shaft tooth, a bearing, an engine, and a clutch.

8. A hydraulic control system according to claim 7, characterized in that the flow distributing spool (11) is connected to a drive motor and to the clutch.

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