CN107588189B - Hydraulic gear shifting control system of double-clutch automatic transmission - Google Patents

Abstract

A hydraulic shift control system for a dual-clutch automatic transmission, comprising a pressure control solenoid valve, a flow control solenoid valve, a first switch solenoid valve, a second switch solenoid valve, a third switch solenoid valve, a fourth switch solenoid valve, a first Gear switch valve, second gear switch valve, third gear switch valve, fourth gear switch valve, first shift cylinder, second shift cylinder, third shift cylinder and fourth shift cylinder, Wherein the four switching solenoid valves respectively control the four gear switching valves to change directions, and the four gear switching valves respectively control the four gear shifting oil cylinders to change gears. This embodiment uses as few combinations of solenoid valves and slide valves as possible to realize the shift control of the automatic transmission with eight gears, and realizes the dual control of shift pressure and flow through the pressure control solenoid valve and flow control solenoid valve, so that The hydraulic system controls the shifting process more accurately, and can better realize the precise control of the shifting process. At the same time, the system is lighter and the control logic is simpler.

Description

Hydraulic Shift Control System of Dual Clutch Automatic Transmission

technical field

The invention relates to the technical field of automatic transmissions, in particular to a hydraulic shift control system of a double-clutch automatic transmission.

Background technique

With the advancement of science and technology, the way automobiles realize shifting has gradually evolved from manual shifting to automatic shifting, and automatic shifting is realized through automatic transmissions. Among them, the dual-clutch automatic transmission has been welcomed by the market due to its advantages such as high transmission efficiency. Two clutches are used in the dual-clutch automatic transmission, one of which is used to control odd-numbered gears, and the other is used to control even-numbered gears. , by automatically switching between the two clutches to complete the shift program, so the power shift during the shift process can be realized, that is, the power is not interrupted during the shift process, and the comfort of the vehicle is improved.

When the automatic transmission realizes automatic shifting, it needs a shift actuator, a system component, whose function is to realize the automatic shift function. At present, hydraulic shift actuators are mostly used. Gear shifting is generally accomplished by a synchronizer keyed to the relevant shaft and rotated therewith. Gears with different transmission ratios are provided on one or both sides of the synchronizer. Under the action of the shift actuator, the synchronizer is The toggle moves axially and engages adjacent gears, coupling the gears to the shaft and synchronizing the gears with the shaft for power output.

The current dual-clutch automatic transmission mostly adopts eight gears (including reverse gear), and utilizes a hydraulic shift control system to control the shift actuator to complete the shifting operation of the eight gears. In the prior art, the combination of electromagnetic valve and spool valve is used as little as possible to realize shift control, and most of the technical solutions are based on pressure control, and it is impossible to precisely control the moving rate of the shift actuator to realize shifting Precise control of the process.

Contents of the invention

The purpose of the present invention is to provide a hydraulic shift control system for a dual-clutch automatic transmission, so as to realize the precise control of the shift actuator during the shift process by combining as few solenoid valves and slide valves as possible, so that the system is more efficient. Lightweight and more concise control logic.

An embodiment of the present invention provides a hydraulic shift control system for a dual-clutch automatic transmission. The hydraulic shift control system includes a pressure control solenoid valve, a flow control solenoid valve, a first switch solenoid valve, a second switch solenoid valve, and a third switch solenoid valve. Solenoid valve, 4th switch solenoid valve, 1st gear switch valve, 2nd gear switch valve, 3rd gear switch valve, 4th gear switch valve, 1st shift cylinder, 2nd shift cylinder, 1st gear The three shift oil cylinders and the fourth shift oil cylinder, wherein the outlet of the pressure control solenoid valve is connected to the inlet of the flow control solenoid valve, the outlet of the flow control solenoid valve is connected to the inlet of the first gear switching valve, the second The inlet of the gear switch valve, the inlet of the third gear switch valve and the inlet of the fourth gear switch valve are connected, the outlet of the first gear switch valve is connected with the oil chamber of the first shift cylinder, and the The outlet of the second gear switching valve is connected with the oil chamber of the second gear shifting cylinder, the outlet of the third gear switching valve is connected with the oil chamber of the third gear shifting oil cylinder, and the outlet of the fourth gear switching valve is It is connected with the oil cavity of the fourth gear shift cylinder, the outlet of the first switch solenoid valve is connected with the control end of the first gear switch valve, and the first gear switch valve is controlled by the first switch solenoid valve for shifting. direction, the outlet of the second switch solenoid valve is connected to the control end of the second gear switch valve, and the second gear switch valve is controlled by the second switch solenoid valve for reversing, and the outlet of the third switch solenoid valve It is connected with the control end of the third gear switch valve, the third gear switch valve is controlled by the third switch solenoid valve for reversing, the outlet of the fourth switch solenoid valve is connected with the control port of the fourth gear switch valve end connection, the fourth gear switch valve is controlled by the fourth switch solenoid valve for reversing, the inlet of the pressure control solenoid valve, the inlet of the first switch solenoid valve, the inlet of the second switch solenoid valve, the second switch solenoid valve Both the inlet of the three-switch solenoid valve and the inlet of the fourth switch solenoid valve are connected to the main oil circuit.

Further, the pressure control solenoid valve has an inlet and an outlet, the flow control solenoid valve has an inlet and two outlets, the inlet of the pressure control solenoid valve is connected to the main oil circuit, and the outlet of the pressure control solenoid valve is connected to the flow control The inlet of the solenoid valve is connected, and the two outlets of the flow control solenoid valve are connected with the first gear switching valve, the second gear switching valve, the third gear switching valve and the fourth gear switching valve.

Further, the flow control solenoid valve can be switched between the first working position and the second working position. When the flow control solenoid valve is in the first working position, the inlet of the flow control solenoid valve and the two ports of the flow control solenoid valve One of the outlets is connected; when the flow control solenoid valve is in the second working position, the inlet of the flow control solenoid valve is connected with the other of the two outlets of the flow control solenoid valve.

Further, the first switch solenoid valve has an inlet and an outlet, the second switch solenoid valve has an inlet and an outlet, the third switch solenoid valve has an inlet and an outlet, the fourth switch solenoid valve has an inlet and an outlet, and the first switch solenoid valve has an inlet and an outlet. The gear switch valve has two inlets, two outlets and one control terminal, the second gear switch valve has two inlets, two outlets and one control terminal, and the third gear switch valve has two inlets, two one outlet and one control terminal, the fourth gear switch valve has two inlets, two outlets and one control terminal, the inlet of the first switch solenoid valve, the inlet of the second switch solenoid valve, the third switch solenoid valve The inlet of the valve and the inlet of the fourth switch solenoid valve are connected with the main oil circuit, the outlet of the first switch solenoid valve is connected with the control terminal of the first gear switch valve, and the outlet of the second switch solenoid valve is connected with the control terminal of the first gear switch valve. The control end of the second gear switch valve is connected, the outlet of the third switch solenoid valve is connected with the control end of the third gear switch valve, and the outlet of the fourth switch solenoid valve is connected with the fourth gear switch valve. The two inlets of the first gear switch valve are respectively connected with the two outlets of the flow control solenoid valve, and the two inlets of the second gear switch valve are respectively connected with the two outlets of the flow control solenoid valve. The two inlets of the third gear switch valve are respectively connected with the two outlets of the flow control solenoid valve, the two inlets of the fourth gear switch valve are respectively connected with the two outlets of the flow control solenoid valve, The two outlets of the first gear switching valve are respectively connected with the two oil chambers of the first gear shifting cylinder, and the two outlets of the second gear switching valve are respectively connected with the two oil chambers of the second gear shifting cylinder. The two outlets of the third gear switching valve are respectively connected with the two oil chambers of the third gear shifting cylinder, and the two outlets of the fourth gear switching valve are respectively connected with the two oil chambers of the fourth gear shifting cylinder. The oil cavity is connected.

Further, the pressure control solenoid valve is a spool type pressure control proportional solenoid valve, the flow control solenoid valve is a spool type flow control proportional solenoid valve, the first gear switching valve, the second gear switching valve . The third gear on-off valve and the fourth gear on-off valve are both spool type hydraulic control reversing valves.

Further, the hydraulic shift control system also includes a first clutch solenoid valve, a second clutch solenoid valve and a clutch safety valve, the first clutch solenoid valve has an inlet and an outlet, the second clutch solenoid valve has an inlet and an outlet, the Both the inlet of the first clutch solenoid valve and the inlet of the second clutch solenoid valve are connected to the main oil circuit. The clutch safety valve has two inlets, two outlets and a control terminal. The two inlets of the clutch safety valve are respectively It is connected with the outlet of the first clutch solenoid valve and the outlet of the second clutch solenoid valve, and the two outlets of the clutch safety valve are respectively connected with the first clutch and the second clutch. The first switch solenoid valve to the fourth switch solenoid valve The outlets of two switching solenoid valves in the valve are simultaneously connected to the control end of the clutch safety valve.

Further, the hydraulic shift control system also includes a fifth switch solenoid valve, a parking control valve and a parking oil cylinder, the fifth switch solenoid valve has an inlet and an outlet, and the parking control valve has an inlet, two outlets and a control valve. The inlet of the fifth switch solenoid valve and the inlet of the parking control valve are connected to the main oil circuit, the outlet of the fifth switch solenoid valve is connected to the control terminal of the parking control valve, and the parking control valve The two outlets of the parking cylinder are respectively connected with the two oil chambers of the parking cylinder.

Further, two switch solenoid valves of the first switch solenoid valve to the fourth switch solenoid valve are integrated into a three-position four-way switch solenoid valve, and the other switch solenoid valves of the first switch solenoid valve to the fourth switch solenoid valve The two on-off solenoid valves are integrated into another three-position four-way on-off solenoid valve.

Further, the hydraulic shift control system also includes a second pressure control solenoid valve and a main oil circuit pressure regulating valve, the second pressure control solenoid valve has an inlet and an outlet, and the main oil circuit pressure regulating valve has an inlet and two outlets and two control ports, the inlet of the second pressure control solenoid valve is connected with the main oil circuit, the outlet of the second pressure control solenoid valve is connected with the first control port of the main oil circuit pressure regulating valve, and the main oil circuit The inlet and the second control port of the pressure regulating valve are connected to the main oil circuit at the same time, the first outlet of the pressure regulating valve of the main oil circuit is connected to the oil tank, and the second outlet of the pressure regulating valve of the main oil circuit leads to the lubricating and cooling oil circuit .

In the embodiment of the present invention, the combination of electromagnetic valves and slide valves as few as possible is used to realize the shift control of the automatic transmission with eight gears, and through the pressure control solenoid valve and the flow control solenoid valve, on the basis of realizing the shift control of the transmission On the one hand, the dual control of shifting pressure and flow is realized, which makes the hydraulic system control the shifting process more precisely, and can better realize the precise control of the shifting process, while reducing the use of slide valves, the system is more portable, and the control logic more concise.

The above description is only an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention, it can be implemented according to the contents of the description, and in order to make the above and other purposes, features and advantages of the present invention more obvious and understandable , the following preferred embodiments are specifically cited below, and are described in detail as follows in conjunction with the accompanying drawings.

Description of drawings

FIG. 1 is a schematic structural diagram of a hydraulic shift control system of a dual-clutch automatic transmission in a first embodiment of the present invention.

FIG. 2 is a schematic structural diagram of a hydraulic shift control system of a dual-clutch automatic transmission in a second embodiment of the present invention.

Detailed ways

In order to further illustrate the technical means and functions adopted by the present invention to achieve the intended invention purpose, the present invention will be described in detail below in conjunction with the accompanying drawings and preferred embodiments.

An embodiment of the present invention provides a hydraulic shift control system for a dual-clutch automatic transmission, with the purpose of using as few combinations of solenoid valves and slide valves as possible to better realize the hydraulic shift control requirements of the automatic transmission.

[first embodiment]

Fig. 1 is a schematic structural view of the hydraulic shift control system of the dual-clutch automatic transmission in the first embodiment of the present invention, please refer to Fig. 1, the hydraulic shift control system includes a pressure control solenoid valve 11, a flow control solenoid valve 21, a first Switch solenoid valve 31, second switch solenoid valve 32, third switch solenoid valve 33, fourth switch solenoid valve 34, first gear switch valve 41, second gear switch valve 42, third gear switch valve 43, The fourth gear switch valve 44 , the first shift oil cylinder 51 , the second shift oil cylinder 52 , the third shift oil cylinder 53 and the fourth shift oil cylinder 54 .

The pressure control solenoid valve 11 has an inlet A1 and an outlet B1, the inlet A1 of the pressure control solenoid valve 11 is connected with the main oil circuit 10, and the outlet B1 of the pressure control solenoid valve 11 is connected with the flow control solenoid valve 21, so that the pressure control solenoid valve 11 The pressure oil output from the outlet B1 can enter the first gear switch valve 41 through the flow control solenoid valve 21 to push the first gear shift cylinder 51 for shifting operation, or enter the second gear switch valve 42 through the flow control solenoid valve 21 to Push the second shift oil cylinder 52 to perform the shift operation, or enter the third gear switch valve 43 through the flow control solenoid valve 21 to push the third shift oil cylinder 53 to perform the shift operation, or enter the fourth gear through the flow control solenoid valve 21 The gear switch valve 44 is used to push the fourth gear shift oil cylinder 54 to perform the gear shifting operation.

When performing shifting operations in different gears, the required shifting pressure is usually different. In order to realize that the shifting pressure output by the outlet B1 of the pressure control solenoid valve 11 can meet the shifting requirements in different gears, in this embodiment, the pressure control solenoid valve 11 is a spool type pressure control proportional solenoid valve, and the pressure The pressure at the outlet B1 of the control solenoid valve 11 is fed back to one end of the pressure control solenoid valve 11 (as shown in FIG. 1 , it is fed back to the spring load end) through the oil circuit. Therefore, when the pressure control solenoid valve 11 is working, the spool of the pressure control solenoid valve 11 can regulate and control the output pressure of the outlet B1 under the joint action of electromagnetic force, spring load force and hydraulic feedback force. That is, by controlling the magnitude of the current input to the electromagnet of the pressure control solenoid valve 11 , the outlet B1 of the pressure control solenoid valve 11 can output different shift pressures under different shift demands.

The flow control solenoid valve 21 has an inlet A2 and two outlets B2, B3 (or called the first outlet B2 and the second outlet B3), the inlet A2 of the flow control solenoid valve 21 is connected with the outlet B1 of the pressure control solenoid valve 11, and the flow rate The two outlets B2 and B3 of the control solenoid valve 21 are connected with the first gear switching valve 41, the second gear switching valve 42, the third gear switching valve 43 and the fourth gear switching valve 44, so that the flow control solenoid valve The pressure oil output from the two outlets B2 and B3 of 21 can push the first gear shift cylinder 51 through the first gear switch valve 41 for gear shifting operation, or push the second gear shift cylinder 52 through the second gear switch valve 42 The gear shifting operation is performed, or the third gear shifting cylinder 53 is pushed through the third gear switch valve 43 to perform the gear shifting operation, and the fourth gear shifting cylinder 54 is pushed through the fourth gear switching valve 44 to perform the gear shifting operation. Specifically, the flow control solenoid valve 21 can be switched between the first working position and the second working position. When the flow control solenoid valve 21 is in the first working position, the inlet A2 of the flow control solenoid valve 21 and the flow control solenoid valve 21 One of the two outlets B2, B3 of the flow control solenoid valve 21 is connected; when the flow control solenoid valve 21 is in the second working position, the inlet A2 of the flow control solenoid valve 21 is connected to the two outlets B2, B3 of the flow control solenoid valve 21 Another connection. In this embodiment, when the flow control solenoid valve 21 is in the first working position (the right position as shown in Figure 1), the inlet A2 of the flow control solenoid valve 21 communicates with the first outlet B2 of the flow control solenoid valve 21; When the flow control solenoid valve 21 is switched to the second working position (the left position shown in FIG. 1 ), the inlet A2 of the flow control solenoid valve 21 communicates with the second outlet B3 of the flow control solenoid valve 21 . That is to say, by changing the working position of the flow control solenoid valve 21, the pressure oil can be selectively guided from the inlet A2 to one of the two outlets B2, B3.

At present, most of the technical solutions for realizing hydraulic shift control are based on pressure control, which cannot accurately control the movement rate of the shift actuator (ie, the shift cylinder) to achieve precise control during the shift process. In order to make the hydraulic system control the gear shifting process more precisely on the basis of shift control, in this embodiment, the flow control solenoid valve 21 is a spool type flow control proportional solenoid valve. Therefore, when the flow control solenoid valve 21 is working, the spool of the flow control solenoid valve 21 can regulate and control the output flow of the two outlets B2 and B3 to a certain extent under the joint action of the electromagnetic force and the spring load force. That is, the flow control solenoid valve 21 can change the current working position of the flow control solenoid valve 21 by adjusting the current value input to the electromagnet of the flow control solenoid valve 21 at each working position (left position or right position). The opening of the lower valve port can be adjusted to adjust the output flow of the two outlets B2 and B3 of the flow control solenoid valve 21, and then realize the control of the moving rate of the shift cylinder, so as to realize the precise control of the shift process.

The first on-off solenoid valve 31 has an inlet A3 and an outlet B4, the second on-off solenoid valve 32 has an inlet A4 and an outlet B5, the third on-off solenoid valve 33 has an inlet A5 and an outlet B6, and the fourth on-off solenoid valve 34 has an inlet A6 and an outlet B7. The first gear switching valve 41 has two inlets A7, A8, two outlets B8, B9 and one control port C1. The second gear switch valve 42 has two inlets A9 , A10 , two outlets B10 , B11 and one control port C2 . The third gear switch valve 43 has two inlets A11, A12, two outlets B12, B13 and one control port C3. The fourth gear switching valve 44 has two inlets A13, A14, two outlets B14, B15 and one control port C4.

The inlet A3 of the first switch solenoid valve 31 is connected to the main oil circuit 10 , and the outlet B4 of the first switch solenoid valve 31 is connected to the control terminal C1 of the first gear switch valve 41 . The inlet A4 of the second switch solenoid valve 32 is connected with the main oil circuit 10 , and the outlet B5 of the second switch solenoid valve 32 is connected with the control terminal C2 of the second gear switch valve 42 . The inlet A5 of the third switching solenoid valve 33 is connected to the main oil circuit 10 , and the outlet B6 of the third switching solenoid valve 33 is connected to the control terminal C3 of the third gear switching valve 43 . The inlet A6 of the fourth switch solenoid valve 34 is connected to the main oil circuit 10 , and the outlet B7 of the fourth switch solenoid valve 34 is connected to the control terminal C4 of the fourth gear switch valve 44 .

The two inlets A7 and A8 of the first gear switching valve 41 are respectively connected with the two outlets B2 and B3 of the flow control solenoid valve 21 . The two inlets A9 and A10 of the second gear switch valve 42 are respectively connected with the two outlets B2 and B3 of the flow control solenoid valve 21 . The two inlets A11 and A12 of the third gear switch valve 43 are respectively connected with the two outlets B2 and B3 of the flow control solenoid valve 21 . The two inlets A13 and A14 of the fourth gear switch valve 44 are respectively connected with the two outlets B2 and B3 of the flow control solenoid valve 21 .

The two outlets B8 and B9 of the first gear switch valve 41 are respectively connected with the two oil chambers of the first shift oil cylinder 51 . The two outlets B10 and B11 of the second gear switch valve 42 are respectively connected with the two oil chambers of the second shift oil cylinder 52 . The two outlets B12 and B13 of the third gear switch valve 43 are respectively connected with the two oil chambers of the third shift oil cylinder 53 . The two outlets B14 and B15 of the fourth gear on-off valve 44 are respectively connected to the two oil chambers of the fourth shift oil cylinder 54 .

The first switch solenoid valve 31 can be switched between the cut-off work position and the conduction work position. When the first switch solenoid valve 31 was in the cut-off work position (right position as shown in Figure 1), the first switch solenoid valve 31 The inlet A3 is disconnected from the outlet B4 of the first switch solenoid valve 31; The outlet B4 of a switching solenoid valve 31 is connected. At this time, the pressure oil from the main oil circuit 10 is applied to the control terminal C1 of the first gear switching valve 41 through the first switching solenoid valve 31 to push the first gear switching valve. 41 for reversing.

The second switch solenoid valve 32 can be switched between the cut-off work position and the conduction work position. When the second switch solenoid valve 32 was in the cut-off work position (right position as shown in Figure 1), the second switch solenoid valve 32 The inlet A4 is disconnected from the outlet B5 of the second switch solenoid valve 32; The outlet B5 of the second switch solenoid valve 32 is connected. At this time, the pressure oil from the main oil circuit 10 is applied to the control end C2 of the second gear switch valve 42 through the second switch solenoid valve 32 to push the second gear switch valve. 42 for reversing.

The third switch solenoid valve 33 can be switched between the cut-off work position and the conduction work position, when the third switch solenoid valve 33 was in the cut-off work position (right position as shown in Figure 1), the third switch solenoid valve 33 The inlet A5 is disconnected from the outlet B6 of the third switch solenoid valve 33; The outlet B6 of the three-switch solenoid valve 33 is connected. At this time, the pressure oil from the main oil circuit 10 is applied to the control terminal C3 of the third gear switch valve 43 through the third switch solenoid valve 33 to push the third gear switch valve. 43 for reversing.

The fourth switch solenoid valve 34 can be switched between the cut-off work position and the conduction work position. When the fourth switch solenoid valve 34 was in the cut-off work position (right position as shown in Figure 1), the fourth switch solenoid valve 34 The inlet A6 is disconnected from the outlet B7 of the fourth switch solenoid valve 34; The outlet B7 of the four-switch solenoid valve 34 is connected. At this time, the pressure oil from the main oil circuit 10 is applied to the control end C4 of the fourth gear switch valve 44 through the fourth switch solenoid valve 34 to push the fourth gear switch valve. 44 for reversing.

In this embodiment, the first gear switch valve 41 is a spool type hydraulically controlled reversing valve. The first gear switching valve 41 can be switched between the first working position and the second working position. When the first gear switching valve 41 was in the first working position (the right position as shown in Figure 1), the first gear The two inlets A7 and A8 of the first gear switch valve 41 are respectively disconnected from the two outlets B8 and B9 of the first gear switch valve 41. At this time, the two outlets B8 and B9 of the first gear switch valve 41 are connected to the fuel tank ; When the first switch solenoid valve 31 is in the conduction working position, the pressure oil from the main oil circuit 10 is applied to the control end C1 of the first gear switch valve 41 through the first switch solenoid valve 31 to push the first gear switch valve When 41 switches to the second working position (the left position as shown in Figure 1), the two inlets A7 and A8 of the first gear switch valve 41 communicate with the two outlets B8 and B9 of the first gear switch valve 41 respectively At this time, the pressure oil from the flow control solenoid valve 21 can pass through the first gear switch valve 41 and enter the first shift oil cylinder 51 to push the first shift oil cylinder 51 to perform the shift operation.

In this embodiment, the second gear switch valve 42 is a spool type hydraulic control reversing valve. The second gear switching valve 42 can be switched between the first working position and the second working position. When the second gear switching valve 42 was in the first working position (the right position as shown in Figure 1), the second gear The two inlets A9 and A10 of the gear switching valve 42 are respectively disconnected from the two outlets B10 and B11 of the second gear switching valve 42, and at this time the two outlets B10 and B11 of the second gear switching valve 42 are connected to the fuel tank ; When the second switch solenoid valve 32 is in the conduction working position, the pressure oil from the main oil circuit 10 is applied to the control end C2 of the second gear switch valve 42 through the second switch solenoid valve 32 to push the second gear switch valve 42 is switched to the second working position (the left position as shown in Figure 1), the two inlets A9 and A10 of the second gear switch valve 42 communicate with the two outlets B10 and B11 of the second gear switch valve 42 respectively At this time, the pressure oil from the second gear switch valve 42 can enter the second shift oil cylinder 52 to push the second shift oil cylinder 52 to perform the shift operation.

In this embodiment, the third gear switch valve 43 is a spool type hydraulically controlled reversing valve. The third gear switching valve 43 can be switched between the first working position and the second working position. When the third gear switching valve 43 was in the first working position (the right position as shown in Figure 1), the third gear The two inlets A11 and A12 of the switch valve 43 are respectively disconnected from the two outlets B12 and B13 of the switch valve 43 for the third gear. At this time, the two outlets B12 and B13 of the switch valve 43 for the third gear are connected to the fuel tank. ; When the third switch solenoid valve 33 is in the conduction working position, the pressure oil from the main oil circuit 10 is applied to the control end C3 of the third gear switch valve 43 through the third switch solenoid valve 33 to push the third gear switch valve When 43 switches to the second working position (the left position as shown in Figure 1), the two inlets A11 and A12 of the third gear switch valve 43 communicate with the two outlets B12 and B13 of the third gear switch valve 43 respectively At this time, the pressure oil from the flow control solenoid valve 21 can pass through the third gear switch valve 43 and enter the third shift oil cylinder 53 to push the third shift oil cylinder 53 to perform the shift operation.

In this embodiment, the fourth gear switch valve 44 is a spool type hydraulically controlled reversing valve. The fourth gear switching valve 44 can be switched between the first working position and the second working position. When the fourth gear switching valve 44 was in the first working position (the right position as shown in Figure 1), the fourth gear The two inlets A13 and A14 of the switch valve 44 are respectively disconnected from the two outlets B14 and B15 of the fourth gear switch valve 44. At this time, the two outlets B14 and B15 of the fourth gear switch valve 44 are connected to the fuel tank ; When the fourth switching solenoid valve 34 is in the conduction working position, the pressure oil from the main oil circuit 10 is applied to the control end C4 of the fourth gear switching valve 44 through the fourth switching solenoid valve 34 to push the fourth gear switching valve 44 is switched to the second working position (the left position as shown in Figure 1), the two inlets A13 and A14 of the fourth gear switch valve 44 communicate with the two outlets B14 and B15 of the fourth gear switch valve 44 respectively At this time, the pressure oil from the fourth gear switch valve 44 can enter the fourth shift oil cylinder 54 to push the fourth shift oil cylinder 54 to perform the shift operation.

As mentioned above, the outlet of the pressure control solenoid valve 11 is connected to the inlet of the flow control solenoid valve 21, and the outlet of the flow control solenoid valve 21 is connected to the inlet of the first gear switch valve 41, the inlet of the second gear switch valve 42, the second gear switch valve 42, and the second gear switch valve. The inlet of the third gear switching valve 43 is connected with the inlet of the fourth gear switching valve 44, the outlet of the first gear switching valve 41 is connected with the oil chamber of the first shift oil cylinder 51, and the outlet of the second gear switching valve 42 It is connected with the oil chamber of the second shift oil cylinder 52, the outlet of the third gear switch valve 43 is connected with the oil chamber of the third shift oil cylinder 53, and the outlet of the fourth gear switch valve 44 is connected with the outlet of the fourth shift oil cylinder 54. The oil chamber is connected, the outlet of the first switch solenoid valve 31 is connected to the control end of the first gear switch valve 41, the first gear switch valve 41 is controlled by the first switch solenoid valve 31 for reversing, and the second switch solenoid valve 32 The outlet of the second gear switch valve 42 is connected to the control end, the second gear switch valve 42 is controlled by the second switch solenoid valve 32 for reversing, the outlet of the third switch solenoid valve 33 is connected to the third gear switch valve 43 The control end of the third gear switch valve 43 is controlled by the third switch solenoid valve 33 to change direction, the outlet of the fourth switch solenoid valve 34 is connected to the control end of the fourth gear switch valve 44, and the fourth gear switch The valve 44 is controlled by the fourth on-off solenoid valve 34 to reversing, the inlet of the pressure control solenoid valve 11, the inlet of the first on-off solenoid valve 31, the inlet of the second on-off solenoid valve 32, the inlet of the third on-off solenoid valve 33 and the first on-off solenoid valve. The inlets of the four-switch solenoid valves 34 are all connected to the main oil circuit 10 .

The pressure control solenoid valve 11 can adjust the inlet pressure of the flow control solenoid valve 21. The flow control solenoid valve 21 can precisely control the outlet pressure and flow according to the inlet pressure. The flow control solenoid valve 21 can also control the reversing of the oil circuit to change Pressure port and drain port. The adjustable inlet pressure can accurately control the outlet pressure and flow according to the inlet pressure, and at the same time, it can also carry out reversing control of the oil circuit to change the pressure oil port and the oil drain port. The first switch solenoid valve 31 can control the opening and closing of the first gear switch valve 41, so that the first shift oil cylinder 51 is connected with the pressure oil port and the oil discharge port of the flow control solenoid valve 21; the second switch solenoid valve 32 can control The opening and closing of the second gear switch valve 42 makes the second shift oil cylinder 52 connect with the pressure oil port and the oil drain port of the flow control solenoid valve 21; the third switch solenoid valve 33 can control the third gear switch valve 43. open and close, so that the third gear shift oil cylinder 53 is connected with the pressure oil port and the oil drain port of the flow control solenoid valve 21; the fourth switch solenoid valve 34 can control the opening and closing of the fourth gear switch valve 44, so that the fourth gear shift The oil cylinder 54 is connected with the pressure oil port and the oil drain port of the flow control solenoid valve 21 .

Therefore, by controlling the pressure control solenoid valve 11 , the flow control solenoid valve 21 and the first switching solenoid valve 31 , the first gear shift cylinder 51 can be moved at a certain rate between the first position and the second position. In this embodiment, it is assumed that the first shift cylinder 51 is used to control the reverse gear and the sixth gear. When the pressure control solenoid valve 11 and the first switch solenoid valve 31 are connected and the flow control solenoid valve 21 is in the first working position (as shown in Figure 1 (right position shown), the pressure oil from the main oil circuit 10 reaches the first outlet B2 of the flow control solenoid valve 21 after the pressure and flow are adjusted through the pressure control solenoid valve 11 and the flow control solenoid valve 21. The position switch valve 41 has switched to the conduction position under the control of the first switch solenoid valve 31, so the pressure oil in the first outlet B2 of the flow control solenoid valve 21 will pass through the first inlet of the first gear switch valve 41 A7 reaches the first outlet B8, and then reaches the left cavity of the first shift cylinder 51, pushes the first shift cylinder 51 to the right and engages the sixth gear; when the pressure control solenoid valve 11 and the first switch solenoid valve 31 are turned on and When the flow control solenoid valve 21 is in the second working position (the left position as shown in Figure 1), the pressure oil from the main oil circuit 10 reaches the flow rate after the pressure and flow adjustment of the pressure control solenoid valve 11 and the flow control solenoid valve 21. The second outlet B3 of the control solenoid valve 21, since the first gear switch valve 41 has switched to the conduction position under the control of the first switch solenoid valve 31, the pressure in the second outlet B3 of the flow control solenoid valve 21 The oil will reach the second outlet B9 through the second inlet A8 of the first gear switching valve 41, and then reach the right cavity of the first gear shift cylinder 51, push the first gear shift cylinder 51 to move left and engage the reverse gear.

By controlling the pressure control solenoid valve 11 , the flow control solenoid valve 21 and the second switch solenoid valve 32 , the second gear shift cylinder 52 can be moved at a certain rate between the first position and the second position. In this embodiment, it is assumed that the second shift cylinder 52 is used to control the 7th gear and the 3rd gear. When the pressure control solenoid valve 11 and the second switch solenoid valve 32 conduct and the flow control solenoid valve 21 is in the first working position (as shown in Figure 1 (right position shown), the pressure oil from the main oil circuit 10 reaches the first outlet B2 of the flow control solenoid valve 21 after the pressure and flow are adjusted through the pressure control solenoid valve 11 and the flow control solenoid valve 21, due to the second gear The position switch valve 42 has been switched to the conduction position under the control of the second switch solenoid valve 32, so the pressure oil in the first outlet B2 of the flow control solenoid valve 21 will pass through the first inlet of the second gear switch valve 42 A9 reaches the first outlet B10, and then reaches the left chamber of the second shift cylinder 52, pushes the second shift cylinder 52 to the right and engages the third gear; when the pressure control solenoid valve 11 and the second switch solenoid valve 32 are turned on and When the flow control solenoid valve 21 is in the second working position (the left position as shown in Figure 1), the pressure oil from the main oil circuit 10 reaches the flow rate after the pressure and flow adjustment of the pressure control solenoid valve 11 and the flow control solenoid valve 21. The second outlet B3 of the control solenoid valve 21, since the second gear switch valve 42 has been switched to the conduction position under the control of the second switch solenoid valve 32, the pressure in the second outlet B3 of the flow control solenoid valve 21 The oil will reach the second outlet B11 through the second inlet A10 of the second gear switching valve 42, and then reach the right cavity of the second shift cylinder 52, push the second shift cylinder 52 to the left and engage the 7th gear.

By controlling the pressure control solenoid valve 11 , the flow control solenoid valve 21 and the third switching solenoid valve 33 , the third gear shift cylinder 53 can be moved at a certain rate between the first position and the second position. In this embodiment, it is assumed that the third shift cylinder 53 is used to control the 2nd gear and the 4th gear. When the pressure control solenoid valve 11 and the third switch solenoid valve 33 conduct and the flow control solenoid valve 21 is in the first working position (as shown in Figure 1 (right position shown), the pressure oil from the main oil circuit 10 reaches the first outlet B2 of the flow control solenoid valve 21 after the pressure and flow are adjusted through the pressure control solenoid valve 11 and the flow control solenoid valve 21, because the third gear The position switch valve 43 has switched to the conduction position under the control of the third switch solenoid valve 33, so the pressure oil in the first outlet B2 of the flow control solenoid valve 21 will pass through the first inlet of the third gear switch valve 43 A11 reaches the first outlet B12, then reaches the left chamber of the third shift oil cylinder 53, pushes the third shift oil cylinder 53 to move to the right and engages the fourth gear; when the pressure control solenoid valve 11 and the third switch solenoid valve 33 conduct and When the flow control solenoid valve 21 is in the second working position (the left position as shown in Figure 1), the pressure oil from the main oil circuit 10 reaches the flow rate after the pressure and flow adjustment of the pressure control solenoid valve 11 and the flow control solenoid valve 21. The second outlet B3 of the control solenoid valve 21, since the third gear switch valve 43 has been switched to the conduction position under the control of the third switch solenoid valve 33, the pressure in the second outlet B3 of the flow control solenoid valve 21 The oil will reach the second outlet B13 through the second inlet A12 of the third gear switching valve 43, and then reach the right cavity of the third shift oil cylinder 53, push the third shift oil cylinder 53 to move left and engage the second gear.

By controlling the pressure control solenoid valve 11 , the flow control solenoid valve 21 and the fourth switching solenoid valve 34 , the fourth gear shift cylinder 54 can be moved at a certain rate between the first position and the second position. In this embodiment, it is assumed that the fourth shift oil cylinder 54 is used to control the fifth gear and the first gear. (right position shown), the pressure oil from the main oil circuit 10 reaches the first outlet B2 of the flow control solenoid valve 21 after the pressure and flow are adjusted through the pressure control solenoid valve 11 and the flow control solenoid valve 21. The position switch valve 44 has switched to the conduction position under the control of the fourth switch solenoid valve 34, so the pressure oil in the first outlet B2 of the flow control solenoid valve 21 will pass through the first inlet of the fourth gear switch valve 44 A13 reaches the first outlet B14, and then reaches the left cavity of the fourth shift oil cylinder 54, pushes the fourth shift oil cylinder 54 to move to the right and engages the first gear; when the pressure control solenoid valve 11 and the fourth switch solenoid valve 34 are turned on and When the flow control solenoid valve 21 is in the second working position (the left position as shown in Figure 1), the pressure oil from the main oil circuit 10 reaches the flow rate after the pressure and flow adjustment of the pressure control solenoid valve 11 and the flow control solenoid valve 21. The second outlet B3 of the control solenoid valve 21, since the fourth gear switching valve 44 has switched to the conduction position under the control of the fourth switch solenoid valve 34, the pressure in the second outlet B3 of the flow control solenoid valve 21 The oil will reach the second outlet B15 through the second inlet A14 of the fourth gear switching valve 44, and then reach the right cavity of the fourth gear shift cylinder 54, and push the fourth gear shift cylinder 54 to move left and engage the fifth gear.

Therefore, in the embodiment of the present invention, the combination of solenoid valves and spool valves as few as possible is used to realize the shift control of the automatic transmission with eight gears, and the pressure control solenoid valve 11 and the flow control solenoid valve 21 are used to realize the shifting control of the transmission. On the basis of gear control, the dual control of gear shift pressure and flow is realized, so that the hydraulic system can control the gear shift process more accurately, and can better realize the precise control of the gear shift process, while reducing the use of slide valves, and the system is more efficient. Lightweight and more concise control logic.

The hydraulic shift control system of this embodiment further includes a main pump 61 , an auxiliary pump 62 and an oil tank 63 . The main pump 61 and the auxiliary pump 62 suck oil from the oil tank 63 through the oil suction filter 64 , so as to provide the pressure oil required for work to the main oil circuit 10 of the hydraulic shift control system. In this embodiment, the main pump 61 is directly driven by the engine of the automobile, and the auxiliary pump 62 is driven by the motor. The supply of pressurized oil in the system is ensured with the engine stopped and thus the main pump 61 stopped. Tank symbols are used in various places in FIG. 1 , and these tank symbols are understood to communicate to tank 63 via associated lines.

In order to prevent the reverse flow of oil, the outlets of the main pump 61 and the auxiliary pump 62 are connected with a one-way valve 65 . In order to control the maximum pressure in the system, the outlet of the main pump 61 is also connected with a system safety valve 66. The system safety valve 66 can be a safety overflow valve or a one-way valve. In this embodiment, the system safety valve 66 is a one-way valve. Connected between the outlet of the main pump 61 and the oil tank 63, the maximum allowable pressure in the system is set through the check valve, and when the pressure in the system exceeds the maximum pressure, the check valve opens to drain oil.

The hydraulic shift control system of this embodiment further includes a first clutch solenoid valve 71 , a second clutch solenoid valve 72 and a clutch safety valve 73 .

The first clutch solenoid valve 71 is used to control engagement or disengagement of the first clutch T1. The first clutch solenoid valve 71 has an inlet A15 and an outlet B16. The inlet A15 of the first clutch solenoid valve 71 is connected to the main oil circuit 10, and the outlet B16 of the first clutch solenoid valve 71 is connected to the clutch safety valve 73. The first clutch solenoid valve 71 can be switched between the cut-off work position and the conduction work position. When the first clutch solenoid valve 71 was in the cut-off work position (right position as shown in FIG. 1 ), the The inlet A15 is disconnected from the outlet B16 of the first clutch solenoid valve 71, and the outlet B16 of the first clutch solenoid valve 71 is connected to the oil tank 63, at this time the first clutch T1 is separated; when the first clutch solenoid valve 71 is in the conduction working position (left position as shown in Figure 1), the inlet A15 of the first clutch solenoid valve 71 communicates with the outlet B16 of the first clutch solenoid valve 71, and at this time, the pressure oil from the main oil circuit 10 passes through the first clutch solenoid valve 71 and the clutch relief valve 73 drive the first clutch T1 to engage.

The second clutch solenoid valve 72 is used to control engagement or disengagement of the second clutch T2. The second clutch solenoid valve 72 has an inlet A16 and an outlet B17 , the inlet A16 of the second clutch solenoid valve 72 is connected to the main oil circuit 10 , and the outlet B17 of the second clutch solenoid valve 72 is connected to the clutch safety valve 73 . The second clutch solenoid valve 72 can be switched between the cut-off work position and the conduction work position. When the second clutch solenoid valve 72 was in the cut-off work position (right position as shown in FIG. 1 ), the The inlet A16 is disconnected from the outlet B17 of the second clutch solenoid valve 72, and the outlet B17 of the second clutch solenoid valve 72 is connected to the fuel tank 63, at this time the second clutch T2 is separated; when the second clutch solenoid valve 72 is in the conduction working position (left position as shown in Figure 1), the inlet A16 of the second clutch solenoid valve 72 communicates with the outlet B17 of the second clutch solenoid valve 72, and at this time, the pressure oil from the main oil circuit 10 passes through the second clutch solenoid valve 72 and clutch relief valve 73 drive the second clutch T2 to engage.

The clutch safety valve 73 is used to disconnect the oil passage leading to the clutches T1 and T2 when the clutches T1 and T2 fail. The clutch safety valve 73 has two inlets A17, A18, two outlets B18, B19 and a control terminal C5, the two inlets A17, A18 of the clutch safety valve 73 are respectively connected with the outlet B16 of the first clutch solenoid valve 71 and the second clutch The outlet B17 of the solenoid valve 72 is connected, the two outlets B18 and B19 of the clutch safety valve 73 are respectively connected with the first clutch T1 and the second clutch T2, and the first switching solenoid valve to the fourth switching solenoid valve 31, 32, 33, 34 The outlets of the two switch solenoid valves are connected to the control port C5 of the clutch safety valve 73 at the same time. In this embodiment, the outlet B4 of the first switch solenoid valve 31 and the outlet B7 of the fourth switch solenoid valve 34 are simultaneously connected to The control terminal C5 of the clutch relief valve 73. The clutch safety valve 73 can be switched between the open position and the closed position. When the clutch safety valve 73 is in the open position (left position as shown in FIG. 1 ), the two inlets A17 and A18 of the clutch safety valve 73 are connected to the clutch safety valve respectively. The two outlets B18 and B19 of the valve 73 are connected. At this time, the engagement or disengagement of the first clutch T1 can be realized by controlling the reversing operation of the first clutch solenoid valve 71, and can be realized by controlling the reversing operation of the second clutch solenoid valve 72. Engagement or disengagement of the second clutch T2; when the clutches T1 and T2 fail, open the first switch solenoid valve 31 and the fourth switch solenoid valve 34 at the same time, so that the first switch solenoid valve 31 and the fourth switch solenoid valve 34 output The pressure oil is applied to the control end C5 of the clutch safety valve 73 at the same time, pushing the clutch safety valve 73 to switch from the open position to the closed position (the right position as shown in Figure 1), at this time, the two inlets A17, A18 is respectively disconnected from the two outlets B18 and B19 of the clutch safety valve 73 , thereby cutting off the oil passages leading to the clutches T1 and T2 . At this time, the first clutch T1 and the second clutch T2 are unloaded through the clutch safety valve 73 .

The hydraulic shift control system of this embodiment further includes a fifth switching solenoid valve 35 , a parking control valve 81 and a parking oil cylinder 82 . The fifth switching solenoid valve 35 has an inlet A19 and an outlet B20. The inlet A19 of the fifth on-off solenoid valve 35 is connected to the main oil circuit 10 , and the outlet B20 of the fifth on-off solenoid valve 35 is connected to the control terminal C6 of the parking control valve 81 . The fifth switch solenoid valve 35 can be switched between the cut-off work position and the conduction work position. When the fifth switch solenoid valve 35 was in the cut-off work position (right position as shown in Figure 1), the fifth switch solenoid valve 35 The inlet A19 is disconnected from the outlet B20 of the fifth switch solenoid valve 35; The outlet B20 of the five-switch solenoid valve 35 is connected. At this time, the pressure oil from the main oil circuit 10 is applied to the control terminal C6 of the parking control valve 81 through the fifth switch solenoid valve 35, so as to push the parking control valve 81 to change direction. .

In this embodiment, the parking control valve 81 is a spool type hydraulic control reversing valve. The parking control valve 81 has an inlet A20, two outlets B21, B22 and a control terminal C6. The inlet A20 of the parking control valve 81 is connected to the main oil circuit 10, and the two outlets B21 and B22 of the parking control valve 81 are respectively connected to the parking The two oil chambers of the vehicle oil cylinder 82 are connected, and the control end C6 of the parking control valve 81 is connected with the outlet B20 of the fifth switching solenoid valve 35 . The parking control valve 81 can be switched between the first working position and the second working position. When the parking control valve 81 is in the first working position (right position as shown in FIG. 1 ), the inlet of the parking control valve 81 A20 communicates with the first outlet B21 of the parking control valve 81, and the second outlet B22 of the parking control valve 81 communicates with the oil tank 63. At this time, the pressure oil from the main oil circuit 10 enters the parking oil cylinder 82 through the parking control valve 81 One of the oil chambers to push the parking cylinder 82 to move to one side; when the fifth switch solenoid valve 35 is in the conducting position, the pressure oil from the main oil circuit 10 is applied to the parking control valve through the fifth switch solenoid valve 35 When the control terminal C6 of 81 pushes the parking control valve 81 to switch to the second working position (the left position as shown in Figure 1), the inlet A20 of the parking control valve 81 communicates with the second outlet B22 of the parking control valve 81 , the first outlet B21 of the parking control valve 81 communicates with the oil tank 63, at this time, the pressure oil from the main oil circuit 10 enters the other oil chamber of the parking oil cylinder 82 through the parking control valve 81 to push the parking oil cylinder 82 to Move to the other side. Therefore, the automatic parking and unlocking functions of the vehicle are realized through the fifth switching solenoid valve 35 , the parking control valve 81 and the parking oil cylinder 82 .

The hydraulic shift control system of this embodiment further includes a second pressure control solenoid valve 12 and a main oil circuit pressure regulating valve 18 .

The second pressure control solenoid valve 12 has an inlet A21 and an outlet B23. The main oil circuit pressure regulating valve 18 has an inlet A22, two outlets B24, B25 (or called the first outlet B24 and the second outlet B25) and two control ports C7, C8 (or called the first control port C7 and the second port Two control terminals C8). The inlet A21 of the second pressure control solenoid valve 12 is connected with the main oil circuit 10, the outlet B23 of the second pressure control solenoid valve 12 is connected with the first control port C7 of the main oil circuit pressure regulating valve 18, and the main oil circuit pressure regulating valve 18 The inlet A22 of the main oil circuit pressure regulating valve 18 and the second control port C8 are connected to the main oil circuit 10 at the same time, the first outlet B24 of the main oil circuit pressure regulating valve 18 is connected to the oil tank 63, and the second outlet B25 of the main oil circuit pressure regulating valve 18 leads to the lubrication cooling The oil circuit is used to lubricate and cool related components (such as bearings, gears, clutches, etc.).

In this embodiment, the second pressure control solenoid valve 12 is a spool type pressure control proportional solenoid valve, and the pressure at the outlet B23 of the second pressure control solenoid valve 12 is fed back to one end of the second pressure control solenoid valve 12 through the oil circuit (Feedback to the solenoid terminal is shown in Figure 1). Therefore, when the second pressure control solenoid valve 12 is working, the spool of the second pressure control solenoid valve 12 can regulate and control the output pressure of the outlet B23 under the joint action of electromagnetic force, spring load force and hydraulic feedback force, Furthermore, the force applied to the first control port C7 of the main oil circuit pressure regulating valve 18 is changed, so that the main oil circuit pressure regulating valve 18 is gradually switched from the closed position to the open position, thereby realizing the control of the oil pressure in the main oil circuit 10 At the same time, the excess oil in the main oil circuit 10 can be sent to the lubricating and cooling oil circuit through the main oil circuit pressure regulating valve 18, so as to meet the needs of cooling the oil and lubricating related components.

In this embodiment, the main oil circuit pressure regulating valve 18 has three working positions. When the output pressure of the outlet B23 of the second pressure control solenoid valve 12 is relatively large, the force acting on the first control port C7 of the main oil circuit pressure regulating valve 18 is also relatively large. In the first working position (the right position as shown in Figure 1), the inlet A22 of the main oil circuit pressure regulating valve 18 is disconnected from the two outlets B24 and B25 of the main oil circuit pressure regulating valve 18; The output pressure of the outlet B23 of the control solenoid valve 12 decreases, and the force acting on the first control port C7 of the main oil circuit pressure regulating valve 18 also decreases. At this time, the second control port acting on the main oil circuit pressure regulating valve 18 The force on the terminal C8 will be greater than the force acting on the first control terminal C7, pushing the main oil circuit pressure regulating valve 18 to switch to the second working position (the middle position as shown in Figure 1), at this time the main oil circuit pressure The inlet A22 of the regulating valve 18 communicates with the second outlet B25 of the main oil circuit pressure regulating valve 18, and the oil can lead to the lubricating and cooling oil circuit through the main oil circuit pressure regulating valve 18; as the second pressure controls the outlet of the solenoid valve 12 The output pressure of B23 continues to decrease, and the main oil circuit pressure regulating valve 18 will switch to the third working position (the left position as shown in Figure 1). At this time, the inlet A22 of the main oil circuit pressure regulating valve 18 and the main oil circuit The two outlets B24 and B25 of the pressure regulating valve 18 are connected, a part of the oil can lead to the lubricating and cooling oil circuit through the main oil circuit pressure regulating valve 18 , and the other part of the oil can return to the oil tank 63 through the main oil circuit pressure regulating valve 18 .

The hydraulic shift control system of this embodiment further includes a third pressure control solenoid valve 13 . The third pressure control solenoid valve 13 has an inlet A23 and an outlet B26. The inlet A23 of the third pressure control solenoid valve 13 is connected to the main oil circuit 10 , and the outlet B26 of the third pressure control solenoid valve 13 is connected to the lubricating and cooling oil circuit.

In this embodiment, the third pressure control solenoid valve 13 is a spool type pressure control proportional solenoid valve, and the pressure at the outlet B26 of the third pressure control solenoid valve 13 is fed back to one end of the third pressure control solenoid valve 13 through the oil circuit (Feedback to the solenoid terminal is shown in Figure 1). Therefore, when the third pressure control solenoid valve 13 is working, the spool of the third pressure control solenoid valve 13 can regulate and control the output pressure of the outlet B26 under the joint action of electromagnetic force, spring load force and hydraulic feedback force.

[Second embodiment]

Fig. 2 is a schematic structural diagram of the hydraulic shift control system of the dual-clutch automatic transmission in the second embodiment of the present invention. The difference between this embodiment and the above-mentioned first embodiment is that in this embodiment, the The four switch solenoid valves 31, 32, 33, 34 are integrated, for example, the first switch solenoid valve 31 and the second switch solenoid valve 32 are integrated into a three-position four-way switch solenoid valve 36, so that the first switch solenoid valve 31 The inlet A3 and the inlet A4 of the second switch solenoid valve 32 are integrated into an inlet A24 of the three-position four-way switch solenoid valve 36 and connected to the main oil circuit 10, and the outlet B4 of the first switch solenoid valve 31 is connected to the second switch solenoid valve. The outlet B5 of the valve 32 is respectively two outlets of the switch solenoid valve 36 of the three-position four-way; the third switch solenoid valve 33 and the fourth switch solenoid valve 34 are integrated into another three-position four-way switch solenoid valve 37, so that The inlet A5 of the third switch solenoid valve 33 and the inlet A6 of the fourth switch solenoid valve 34 are integrated into an inlet A25 of the switch solenoid valve 37 of the three-position four-way and connected with the main oil circuit 10, the third switch solenoid valve 33 The outlet B6 and the outlet B7 of the fourth switch solenoid valve 34 are respectively two outlets of the three-position four-way switch solenoid valve 37 .

The switch solenoid valve 36 of the first three-position four-way can be switched between the cut-off position, the first work position and the second work position. In neutral position), the inlet A24 of the switch solenoid valve 36 is disconnected from the first outlet B4 and the second outlet B5 of the switch solenoid valve 36, and at this time the first outlet B4 of the switch solenoid valve 36 is connected with the second outlet B5 To the oil tank; when the switch solenoid valve 36 is switched to the first working position (right position as shown in Figure 2), the inlet A24 of the switch solenoid valve 36 communicates with the first outlet B4 of the switch solenoid valve 36, at this time the switch solenoid valve The second outlet B5 of the switch solenoid valve 36 is connected to the oil tank; when the switch solenoid valve 36 is switched to the second working position (the left position as shown in Figure 2), the inlet A24 of the switch solenoid valve 36 and the second outlet B5 of the switch solenoid valve 36 The first outlet B4 of the switch solenoid valve 36 is connected to the oil tank. That is to say, by changing the working position of the switching solenoid valve 36, the pressure oil can be selectively guided from the inlet A24 to one of the two outlets B4, B5, so the first switch in the above-mentioned first embodiment can be The solenoid valve 31 and the second switch solenoid valve 32 are integrated into one switch solenoid valve, which further simplifies the number of slide valves and reduces the cost.

The second three-position four-way switching solenoid valve 37 can be switched between the cut-off position, the first working position and the second working position. In neutral position), the inlet A24 of the switch solenoid valve 37 is disconnected from the first outlet B6 and the second outlet B7 of the switch solenoid valve 37, and at this time the first outlet B6 and the second outlet B7 of the switch solenoid valve 37 are connected. to the fuel tank; when the switch solenoid valve 37 is switched to the first working position (the right position as shown in Figure 2), the inlet A24 of the switch solenoid valve 37 communicates with the first outlet B6 of the switch solenoid valve 37, and the switch solenoid valve The second outlet B7 of the switch solenoid valve 37 is connected to the oil tank; when the switch solenoid valve 37 is switched to the second working position (the left position as shown in Figure 2), the inlet A24 of the switch solenoid valve 37 and the second outlet B7 of the switch solenoid valve 37 The first outlet B6 of the switch solenoid valve 37 is connected to the oil tank. That is to say, by changing the working position of the switching solenoid valve 37, the pressure oil can be selectively guided from the inlet A24 to one of the two outlets B6, B7, so the third switch in the above-mentioned first embodiment can be The solenoid valve 33 and the fourth switch solenoid valve 34 are integrated into one switch solenoid valve, which further simplifies the number of slide valves and reduces the cost.

For other structures and working principles of this embodiment, reference may be made to the above-mentioned first embodiment, which will not be repeated here.

The above description is only a preferred embodiment of the present invention, and does not limit the present invention in any form. Although the present invention has been disclosed as above with preferred embodiments, it is not intended to limit the present invention. Anyone familiar with this field Those skilled in the art, without departing from the scope of the technical solution of the present invention, may use the technical content disclosed above to make some changes or modify them into equivalent embodiments with equivalent changes, but as long as they do not depart from the technical solution of the present invention, the Technical Essence Any simple modifications, equivalent changes and modifications made to the above embodiments still fall within the scope of the technical solution of the present invention.

Claims (8)

1. A hydraulic shift control system of a dual clutch automatic transmission, characterized in that the hydraulic shift control system includes a pressure control solenoid valve (11), a flow control solenoid valve (21), a first on-off solenoid valve (31), a second on-off solenoid valve (32), a third on-off solenoid valve (33), a fourth on-off solenoid valve (34), a first shift switching valve (41), a second shift switching valve (42), a third shift switching valve (43), a fourth shift switching valve (44), a first shift cylinder (51), a second shift cylinder (52), a third shift cylinder (53) and a fourth shift cylinder (54), wherein an outlet of the pressure control solenoid valve (11) is connected to an inlet of the flow control solenoid valve (21), an outlet of the flow control solenoid valve (21) is connected to an inlet of the first shift switching valve (41), an inlet of the second shift cylinder (42), an inlet of the third shift switching valve (43) and an inlet of the fourth shift cylinder (44), an outlet of the first shift switching valve (41) is connected to an outlet of the second shift cylinder (51), an outlet of the fourth shift cylinder (44) is connected to an outlet of the fourth shift cylinder (52), an outlet of the second shift cylinder (51) is connected to an outlet of the second shift cylinder (52), an outlet of the first switching solenoid valve (31) is connected with a control end of the first gear switching valve (41), the first gear switching valve (41) is controlled by the first switching solenoid valve (31) to perform reversing, an outlet of the second switching solenoid valve (32) is connected with a control end of the second gear switching valve (42), the second gear switching valve (42) is controlled by the second switching solenoid valve (32) to perform reversing, an outlet of the third switching solenoid valve (33) is connected with a control end of the third gear switching valve (43), the third gear switching valve (43) is controlled by the third switching solenoid valve (33) to perform reversing, an outlet of the fourth switching solenoid valve (34) is connected with a control end of the fourth gear switching valve (44), the fourth gear switching valve (44) is controlled by the fourth switching solenoid valve (34) to perform reversing, an inlet of the pressure control solenoid valve (11), an inlet of the first switching solenoid valve (31), an inlet of the second switching solenoid valve (32), and an inlet of the fourth switching solenoid valve (10) are connected with an oil path;

the hydraulic shift control system further includes a second pressure control solenoid valve (12) and a main oil passage pressure regulating valve (18), the second pressure control solenoid valve (12) having an inlet (a 21) and an outlet (B23), the main oil passage pressure regulating valve (18) having an inlet (a 22), two outlets (B24, B25) and two control ends (C7, C8), the inlet (a 21) of the second pressure control solenoid valve (12) being connected to the main oil passage (10), the outlet (B23) of the second pressure control solenoid valve (12) being connected to the first control end (C7) of the main oil passage pressure regulating valve (18), the inlet (a 22) and the second control end (C8) of the main oil passage pressure regulating valve (18) being simultaneously connected to the main oil passage (10), the first outlet (B24) of the main oil passage pressure regulating valve (18) being connected to an oil tank (63), the second outlet (B25) of the main oil passage pressure regulating valve (18) being connected to a lubricating cooling oil passage.

2. The hydraulic shift control system of a dual clutch automatic transmission according to claim 1, characterized in that the pressure control solenoid valve (11) has an inlet (A1) and an outlet (B1), the flow control solenoid valve (21) has an inlet (A2) and two outlets (B2, B3), the inlet (A1) of the pressure control solenoid valve (11) is connected to the main oil passage (10), the outlet (B1) of the pressure control solenoid valve (11) is connected to the inlet (A2) of the flow control solenoid valve (21), and the two outlets (B2, B3) of the flow control solenoid valve (21) are connected to the first gear switching valve (41), the second gear switching valve (42), the third gear switching valve (43), and the fourth gear switching valve (44).

3. The hydraulic shift control system of a dual clutch automatic transmission as set forth in claim 2, characterized in that the flow control solenoid valve (21) is switchable between a first operating position and a second operating position, and when the flow control solenoid valve (21) is in the first operating position, the inlet (A2) of the flow control solenoid valve (21) is communicated with one of the two outlets (B2, B3) of the flow control solenoid valve (21); when the flow control electromagnetic valve (21) is in the second working position, the inlet (A2) of the flow control electromagnetic valve (21) is communicated with the other of the two outlets (B2, B3) of the flow control electromagnetic valve (21).

4. The hydraulic shift control system of a double clutch automatic transmission according to claim 2, characterized in that the first switching solenoid valve (31) has an inlet (A3) and an outlet (B4), the second switching solenoid valve (32) has an inlet (A4) and an outlet (B5), the third switching solenoid valve (33) has an inlet (A5) and an outlet (B6), the fourth switching solenoid valve (34) has an inlet (A6) and an outlet (B7), the first gear switching valve (41) has two inlets (A7, A8), two outlets (B8, B9) and one control terminal (C1), the second gear switching valve (42) has two inlets (A9, a 10), two outlets (B10, B11) and one control terminal (C2), the third gear switching valve (43) has two inlets (a 11, a 12), two outlets (B12, B13) and one control terminal (C3), the fourth gear switching valve (44) has two inlets (a 11, a 12), two outlets (B12, B13) and one control terminal (C3), the fourth switching solenoid valve (32) has two inlets (A6, A4), the first switching solenoid valve (A3), the second switching solenoid valve (34) and the fourth switching valve (34) connected to the inlet (A3), the second switching solenoid valve (14, B6), an outlet (B4) of the first switching electromagnetic valve (31) is connected with a control end (C1) of the first gear switching valve (41), an outlet (B5) of the second switching electromagnetic valve (32) is connected with a control end (C2) of the second gear switching valve (42), an outlet (B6) of the third switching electromagnetic valve (33) is connected with a control end (C3) of the third gear switching valve (43), an outlet (B7) of the fourth switching electromagnetic valve (34) is connected with a control end (C4) of the fourth gear switching valve (44), two inlets (A7, A8) of the first gear switching valve (41) are respectively connected with two outlets (B2, B3) of the flow control electromagnetic valve (21), two inlets (A9, A10) of the second gear switching valve (42) are respectively connected with two outlets (B2, B3) of the flow control electromagnetic valve (21), two inlets (A9, B10) of the third gear switching valve (43) are respectively connected with two outlets (B2, B3) of the flow control electromagnetic valve (21), two inlets (A2, B3) of the first gear switching valve (11) are respectively connected with two outlets (B2, B3) of the flow control electromagnetic valve (13) of the first gear switching valve (11), two outlets (B10, B11) of the second gear switch valve (42) are respectively connected with two oil cavities of the second gear shifting cylinder (52), two outlets (B12, B13) of the third gear switch valve (43) are respectively connected with two oil cavities of the third gear shifting cylinder (53), and two outlets (B14, B15) of the fourth gear switch valve (44) are respectively connected with two oil cavities of the fourth gear shifting cylinder (54).

5. The hydraulic shift control system of a dual clutch automatic transmission according to claim 4, characterized in that the pressure control solenoid valve (11) is a spool type pressure control proportional solenoid valve, the flow control solenoid valve (21) is a spool type flow control proportional solenoid valve, and the first gear switching valve (41), the second gear switching valve (42), the third gear switching valve (43), and the fourth gear switching valve (44) are all spool type pilot operated directional control valves.

6. A hydraulic shift control system of a dual clutch automatic transmission as claimed in claim 4, the hydraulic shift control system further includes a first clutch solenoid valve (71), a second clutch solenoid valve (72), and a clutch relief valve (73), the first clutch solenoid valve (71) having an inlet (A15) and an outlet (B16), the second clutch solenoid valve (72) having an inlet (A16) and an outlet (B17), an inlet (A15) of the first clutch solenoid valve (71) and an inlet (A16) of the second clutch solenoid valve (72) are both connected to the main oil passage (10), the clutch safety valve (73) has two inlets (A17, A18), two outlets (B18, B19) and a control end (C5), the two inlets (A17, A18) of the clutch safety valve (73) are respectively connected with the outlet (B16) of the first clutch electromagnetic valve (71) and the outlet (B17) of the second clutch electromagnetic valve (72), the two outlets (B18, B19) of the clutch safety valve (73) are respectively connected with the first clutch (T1) and the second clutch (T2), outlets of two of the first to fourth switching solenoid valves (31, 32, 33, 34) are simultaneously connected to a control terminal (C5) of the clutch relief valve (73).

7. The hydraulic shift control system of a dual clutch automatic transmission according to claim 4, characterized by further comprising a fifth switching solenoid valve (35), a parking control valve (81) and a parking cylinder (82), the fifth switching solenoid valve (35) having an inlet (A19) and an outlet (B20), the parking control valve (81) having an inlet (A20), two outlets (B21, B22) and a control end (C6), the inlet (A19) of the fifth switching solenoid valve (35) and the inlet (A20) of the parking control valve (81) being connected to the main oil passage (10), the outlet (B20) of the fifth switching solenoid valve (35) being connected to the control end (C6) of the parking control valve (81), the two outlets (B21, B22) of the parking control valve (81) being connected to the two oil chambers of the parking cylinder (82), respectively.

8. The hydraulic shift control system of a dual clutch automatic transmission according to claim 4, characterized in that two of the first to fourth switching solenoids (31, 32, 33, 34) are integrated into one three-position four-way switching solenoid (36), and the other two of the first to fourth switching solenoids (31, 32, 33, 34) are integrated into the other three-position four-way switching solenoid (37).

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