CN107588188B - Hydraulic gear-shifting control system of double-clutch automatic transmission - Google Patents

Abstract

A hydraulic gear-shifting control system of a double-clutch automatic transmission comprises a first pressure control electromagnetic valve, a second pressure control electromagnetic valve, a first flow control electromagnetic valve, a second flow control electromagnetic valve, a first switch electromagnetic valve, a second switch electromagnetic valve, a first gear switch valve, a second gear switch valve, a third gear switch valve, a fourth gear switch valve, a first gear shifting oil cylinder, a second gear shifting oil cylinder, a third gear shifting oil cylinder and a fourth gear shifting oil cylinder, wherein the four gear switch valves are used for respectively controlling the four gear shifting oil cylinders to shift gears. This embodiment adopts as few solenoid valves and spool valve combination as possible, realizes the automatic gearbox shift control of eight fender position, has realized the dual control of pressure and flow of shifting through two pressure control solenoid valves and two flow control solenoid valves moreover, makes hydraulic system more accurate to the process control that shifts, can realize the accurate control of the process of shifting better, has also improved the security in the aspect of preventing the mistake and engaging a gear.

Description

Hydraulic gear-shifting control system of double-clutch automatic transmission

Technical Field

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

Background

With the advancement of technology, the way of realizing speed change of automobiles gradually evolves from manual speed change to automatic speed change, and the automatic speed change is realized through an automatic transmission. The double-clutch automatic transmission is popular in the market due to the advantages of high transmission efficiency and the like, the double-clutch automatic transmission adopts two clutches, one clutch is used for controlling odd gears, the other clutch is used for controlling even gears, and a gear shifting program is completed by automatically switching between the two clutches, so that power gear shifting in the gear shifting process can be realized, namely, power is not interrupted in the gear shifting process, and the running comfort of a vehicle is improved.

When the automatic transmission realizes automatic gear shifting, a gear shifting actuating mechanism is needed as a system part, the function of the automatic gear shifting is realized, and a hydraulic gear shifting actuating mechanism is mostly adopted at present. Shifting is generally accomplished by a synchronizer keyed to and rotating with an associated shaft, provided on one or both sides with gears providing different gear ratios, which is shifted axially and into engagement with adjacent gears under the action of a shift actuator, coupling the gears to the shaft to achieve gear to shaft synchronization, and thereby output power.

The existing double-clutch automatic transmission mostly adopts eight gears (including reverse gears), and a hydraulic gear shifting control system is used for controlling a gear shifting actuating mechanism so as to complete gear shifting operation of the eight gears. In the prior art, gear shifting control is realized by using the combination of electromagnetic valves and slide valves as few as possible, wherein most technical schemes mainly adopt pressure control, and the movement rate of a gear shifting actuating mechanism cannot be accurately controlled so as to realize the accurate control of a gear shifting process; and, can also make improvement to preventing the mistake from putting into gear.

Disclosure of Invention

The invention aims to provide a hydraulic gear shifting control system of a double-clutch automatic transmission, which realizes the accurate control of a gear shifting actuating mechanism in the gear shifting process by combining electromagnetic valves and slide valves as few as possible and simultaneously improves the safety of preventing mistaken gear shifting.

The embodiment of the invention provides a hydraulic gear-shifting control system of a double-clutch automatic transmission, which comprises a first pressure control electromagnetic valve, a second pressure control electromagnetic valve, a first flow control electromagnetic valve, a second flow control electromagnetic valve, a first switch electromagnetic valve, a second switch electromagnetic valve, a first gear switch valve, a second gear switch valve, a third gear switch valve, a fourth gear switch valve, a first gear oil cylinder, a second gear oil cylinder, a third gear oil cylinder and a fourth gear oil cylinder, wherein the outlet of the first pressure control electromagnetic valve is connected with the inlet of the first flow control electromagnetic valve, the outlet of the second pressure control electromagnetic valve is connected with the inlet of the second flow control electromagnetic valve, the outlet of the first flow control electromagnetic valve is connected with the inlet of the first gear switch valve and the inlet of the third gear switch valve, the outlet of the second flow control electromagnetic valve is connected with the inlet of the second gear switch valve and the inlet of the fourth gear switch valve, the outlet of the first gear switch valve is connected with the oil cavity of the first gear shifting oil cylinder, the outlet of the second gear switch valve is connected with the oil cavity of the second gear shifting oil cylinder, the outlet of the third gear switch valve is connected with the oil cavity of the third gear shifting oil cylinder, the outlet of the fourth gear switch valve is connected with the oil cavity of the fourth gear shifting oil cylinder, the outlet of the first switch electromagnetic valve is connected with the control end of the first gear switch valve and the control end of the second gear switch valve, the first gear switch valve and the second gear switch valve are controlled by the first switch electromagnetic valve to change direction, the outlet of the second switch electromagnetic valve is connected with the control end of the third gear switch valve and the control end of the fourth gear switch valve, the third gear switch valve and the fourth gear switch valve are controlled by the second switch electromagnetic valve to change direction, the inlet of the first pressure control solenoid valve, the inlet of the second pressure control solenoid valve, the inlet of the first switching solenoid valve and the inlet of the second switching solenoid valve are all connected with a main oil path.

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

Further, the first flow control electromagnetic valve can be switched between a first working position and a second working position, when the first flow control electromagnetic valve is in the first working position, the inlet of the first flow control electromagnetic valve is communicated with one of the two outlets of the first flow control electromagnetic valve; when the first flow control electromagnetic valve is at the second working position, the inlet of the first flow control electromagnetic valve is communicated with the other of the two outlets of the first flow control electromagnetic valve.

Further, the second flow control electromagnetic valve can be switched between a first working position and a second working position, when the second flow control electromagnetic valve is in the first working position, the inlet of the second flow control electromagnetic valve is communicated with one of the two outlets of the second flow control electromagnetic valve; when the second flow control electromagnetic valve is at the second working position, the inlet of the second flow control electromagnetic valve is communicated with the other of the two outlets of the second flow control electromagnetic valve.

Further, the first on-off solenoid valve has an inlet and an outlet, the second on-off solenoid valve has an inlet and an outlet, the first gear switch valve has two inlets, two outlets and a control end, the second gear switch valve has two inlets, two outlets and a control end, the third gear switch valve has two inlets, two outlets and a control end, the fourth gear switch valve has two inlets, two outlets and a control end, the inlet of the first switch electromagnetic valve and the inlet of the second switch electromagnetic valve are both connected with the main oil way, the outlet of the first switch electromagnetic valve is simultaneously connected with the control end of the first gear switch valve and the control end of the second gear switch valve, the outlet of the second switch electromagnetic valve is simultaneously connected with the control end of the third gear switch valve and the control end of the fourth gear switch valve, two inlets of the first gear switch valve are respectively connected with two outlets of the first flow control electromagnetic valve, two inlets of the second gear switch valve are respectively connected with two outlets of the second flow control electromagnetic valve, two inlets of the third gear switch valve are respectively connected with two outlets of the first flow control electromagnetic valve, two inlets of the fourth gear switch valve are respectively connected with two outlets of the second flow control electromagnetic valve, two outlets of the first gear switch valve are respectively connected with two oil cavities of the first gear shifting oil cylinder, two outlets of the second gear switch valve are respectively connected with two oil cavities of the second gear shifting oil cylinder, two outlets of the third gear switch valve are respectively connected with two oil cavities of the third gear shifting oil cylinder, two outlets of the fourth gear switch valve are respectively connected with two oil cavities of the fourth gear shifting oil cylinder.

Further, the first pressure control solenoid valve and the second pressure control solenoid valve are both slide valve type pressure control proportional solenoid valves, the first flow control solenoid valve and the second flow control solenoid valve are both slide valve type flow control proportional solenoid valves, and the first gear switch valve, the second gear switch valve, the third gear switch valve and the fourth gear switch valve are all slide valve type hydraulic control directional control valves.

Further, the hydraulic gear shifting control system further comprises a first clutch solenoid valve, a second clutch solenoid valve and a clutch safety valve, wherein the first clutch solenoid valve is provided with an inlet and an outlet, the second clutch solenoid valve is provided with an inlet and an outlet, the inlet of the first clutch solenoid valve and the inlet of the second clutch solenoid valve are both connected with the main oil path, the clutch safety valve is provided with two inlets, two outlets and a control end, the two inlets of the clutch safety valve are respectively connected with the outlet of the first clutch solenoid valve and the outlet of the second clutch solenoid valve, the two outlets of the clutch safety valve are respectively connected with the first clutch and the second clutch, and the outlet of the first switch solenoid valve and the outlet of the second switch solenoid valve are simultaneously connected with the control end of the clutch safety valve.

Further, the hydraulic gear shifting control system further comprises a third switch electromagnetic valve, a parking control valve and a parking oil cylinder, wherein the third switch electromagnetic valve is provided with an inlet and an outlet, the parking control valve is provided with an inlet, two outlets and a control end, the inlet of the third switch electromagnetic valve and the inlet of the parking control valve are both connected with the main oil way, the outlet of the third switch electromagnetic valve is connected with the control end of the parking control valve, and the two outlets of the parking control valve are respectively connected with two oil cavities of the parking oil cylinder.

Furthermore, the first switching solenoid valve and the second switching solenoid valve are integrated into a three-position four-way switching solenoid valve, the inlet of the first switching solenoid valve and the inlet of the second switching solenoid valve are integrated into one inlet of the three-position four-way switching solenoid valve and are connected with the main oil path, and the outlet of the first switching solenoid valve and the outlet of the second switching solenoid valve are respectively two outlets of the three-position four-way switching solenoid valve.

Further, the hydraulic gear-shifting control system further comprises a third pressure control solenoid valve and a main oil circuit pressure regulating valve, wherein the third pressure control solenoid valve is provided with an inlet and an outlet, the main oil circuit pressure regulating valve is provided with an inlet, two outlets and two control ends, the inlet of the third pressure control solenoid valve is connected with the main oil circuit, the outlet of the third pressure control solenoid valve is connected with the first control end of the main oil circuit pressure regulating valve, the inlet and the second control end of the main oil circuit pressure regulating valve are simultaneously connected with the main oil circuit, the first outlet of the main oil circuit pressure regulating valve is connected with an oil tank, and the second outlet of the main oil circuit pressure regulating valve is communicated with a lubricating and cooling oil circuit.

In the embodiment of the invention, the gear shifting control of the automatic transmission with eight gears is realized by adopting the combination of the electromagnetic valves and the slide valves as few as possible, and the double control of the gear shifting pressure and the flow is realized on the basis of realizing the gear shifting control of the transmission through the two pressure control electromagnetic valves and the two flow control electromagnetic valves, so that the hydraulic system can control the gear shifting process more accurately, and the accurate control of the gear shifting process can be better realized. In addition, the embodiment of the invention can also effectively avoid simultaneously engaging a plurality of odd gears or a plurality of even gears, and also improve the safety in the aspect of preventing mistaken engaging.

The foregoing description is only an overview of the technical solutions of the present invention, and in order to make the technical means of the present invention more clearly understood, the present invention may be implemented in accordance with the content of the description, and in order to make the above and other objects, features, and advantages of the present invention more clearly understood, the following preferred embodiments are described in detail with reference to the accompanying drawings.

Drawings

Fig. 1 is a schematic configuration diagram of a hydraulic shift control system of a dual clutch automatic transmission according to 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 according to a second embodiment of the present invention.

Detailed Description

To further illustrate the technical means and effects of the present invention adopted to achieve the predetermined objects, the present invention will be described in detail below with reference to the accompanying drawings and preferred embodiments.

The embodiment of the invention provides a hydraulic gear shifting control system for a double-clutch automatic transmission, aiming at better meeting the hydraulic gear shifting control requirement of the automatic transmission by using the combination of electromagnetic valves and slide valves as few as possible.

[ first embodiment ]

Fig. 1 is a schematic structural diagram of a hydraulic shift control system of a dual clutch automatic transmission according to a first embodiment of the present invention, referring to fig. 1, the hydraulic shift control system includes a first pressure control solenoid valve 11, a second pressure control solenoid valve 12, a first flow control solenoid valve 21, a second flow control solenoid valve 22, a first switching solenoid valve 31, a second switching solenoid valve 32, a first gear switching valve 41, a second gear switching valve 42, a third gear switching valve 43, a fourth gear switching valve 44, a first shift cylinder 51, a second shift cylinder 52, a third shift cylinder 53 and a fourth shift cylinder 54.

The first pressure control solenoid valve 11 has an inlet A1 and an outlet B1, the inlet A1 of the first pressure control solenoid valve 11 is connected to the main oil passage 10, and the outlet B1 of the first pressure control solenoid valve 11 is connected to the first flow control solenoid valve 21, so that the pressure oil output from the outlet B1 of the first pressure control solenoid valve 11 can enter the first shift position switching valve 41 via the first flow control solenoid valve 21 to push the first shift cylinder 51 to perform a shifting operation, or enter the third shift position switching valve 43 via the first flow control solenoid valve 21 to push the third shift cylinder 53 to perform a shifting operation.

The required shift pressure will usually be different when shifting is performed in different gears. In order to realize that the shifting pressure output by the outlet B1 of the first pressure control electromagnetic valve 11 can meet the shifting requirement under different gears, in this embodiment, the first pressure control electromagnetic valve 11 is a slide valve type pressure control proportional electromagnetic valve, and the pressure of the outlet B1 of the first pressure control electromagnetic valve 11 is fed back to one end of the first pressure control electromagnetic valve 11 through an oil path (shown in fig. 1 as being fed back to a spring load end). Therefore, when the first pressure control solenoid valve 11 is operated, the spool of the first pressure control solenoid valve 11 can regulate and control the output pressure of the outlet B1 under the combined action of the electromagnetic force, the spring load force and the hydraulic feedback force. That is, by controlling the value of the current input to the electromagnet of the first pressure control electromagnetic valve 11, the outlet B1 of the first pressure control electromagnetic valve 11 can output different shift pressures under different shift requirements.

The second pressure control solenoid valve 12 has an inlet A2 and an outlet B2, the inlet A2 of the second pressure control solenoid valve 12 is connected to the main oil passage 10, and the outlet B2 of the second pressure control solenoid valve 12 is connected to the second flow control solenoid valve 22, so that the pressure oil output from the outlet B2 of the second pressure control solenoid valve 12 can enter the second shift position switching valve 42 via the second flow control solenoid valve 22 to push the second shift cylinder 52 to perform a shifting operation, or enter the fourth shift position switching valve 44 via the second flow control solenoid valve 22 to push the fourth shift cylinder 54 to perform a shifting operation.

The required shift pressure will usually be different when shifting is performed in different gears. In order to realize that the shift pressure output by the outlet B2 of the second pressure control electromagnetic valve 12 can meet the shift requirement in different gears, in this embodiment, the second pressure control electromagnetic valve 12 is a slide valve type pressure control proportional electromagnetic valve, and the pressure of the outlet B2 of the second pressure control electromagnetic valve 12 is fed back to one end of the second pressure control electromagnetic valve 12 (shown in fig. 1 as being fed back to the spring load end) through an oil path. Therefore, when the second pressure control solenoid valve 12 is operated, the spool of the second pressure control solenoid valve 12 can regulate and control the output pressure of the outlet B2 under the combined action of the electromagnetic force, the spring load force and the hydraulic feedback force. That is, by controlling the magnitude of the current value input to the electromagnet of the second pressure control solenoid valve 12, it is possible to realize that the outlet B2 of the second pressure control solenoid valve 12 outputs different shift pressures under different shift demands.

The first flow control solenoid valve 21 has an inlet A3 and two outlets B3 and B4 (or referred to as a first outlet B3 and a second outlet B4), the inlet A3 of the first flow control solenoid valve 21 is connected to the outlet B1 of the first pressure control solenoid valve 11, and the two outlets B3 and B4 of the first flow control solenoid valve 21 are connected to the first shift switch valve 41 and the third shift switch valve 43, so that the pressurized oil output from the two outlets B3 and B4 of the first flow control solenoid valve 21 can push the first shift cylinder 51 through the first shift switch valve 41 to perform a shift operation, or push the third shift cylinder 53 through the third shift switch valve 43 to perform a shift operation. Specifically, the first flow control solenoid valve 21 is switchable between a first operating position and a second operating position, and when the first flow control solenoid valve 21 is in the first operating position, the inlet A3 of the first flow control solenoid valve 21 communicates with one of the two outlets B3, B4 of the first flow control solenoid valve 21; when the first flow rate control solenoid valve 21 is in the second operating position, the inlet A3 of the first flow rate control solenoid valve 21 communicates with the other of the two outlets B3, B4 of the first flow rate control solenoid valve 21. In the present embodiment, when the first flow control solenoid valve 21 is in the first operating position (right position as shown in fig. 1), the inlet A3 of the first flow control solenoid valve 21 communicates with the first outlet B3 of the first flow control solenoid valve 21; when the first flow rate control solenoid valve 21 is switched to the second operating position (the left position as viewed in fig. 1), the inlet A3 of the first flow rate control solenoid valve 21 communicates with the second outlet B4 of the first flow rate control solenoid valve 21. That is, by changing the operating position of the first flow rate control solenoid valve 21, it is possible to selectively direct the pressure oil from the inlet A3 to one of the two outlets B3, B4.

At present, most technical schemes for realizing hydraulic gear shifting control mainly adopt pressure control, and the moving speed of a gear shifting actuating mechanism (namely a gear shifting oil cylinder) cannot be accurately controlled so as to realize accurate control in the gear shifting process. In order to make the hydraulic system control the gear shifting process more accurately based on the gear shifting control, in the present embodiment, the first flow control electromagnetic valve 21 is a spool type flow control proportional electromagnetic valve. Therefore, when the first flow control solenoid valve 21 is in operation, the spool of the first flow control solenoid valve 21 can regulate and control the output flow of the two outlets B3 and B4 to a certain extent under the combined action of the electromagnetic force and the spring load force. That is, the first flow control electromagnetic valve 21 can change the valve opening of the first flow control electromagnetic valve 21 at the current working position by adjusting the current value input to the electromagnet of the first flow control electromagnetic valve 21 at each working position (left or right), so as to adjust the output flow of the two outlets B3 and B4 of the first flow control electromagnetic valve 21, and further control the movement rate of the shift cylinder, so as to realize the accurate control of the shift process.

The second flow control solenoid valve 22 has an inlet A4 and two outlets B5 and B6 (or referred to as a first outlet B5 and a second outlet B6), the inlet A4 of the second flow control solenoid valve 22 is connected to the outlet B2 of the second pressure control solenoid valve 12, and the two outlets B5 and B6 of the second flow control solenoid valve 22 are connected to the second shift position switch valve 42 and the fourth shift position switch valve 44, so that the pressure oil output from the two outlets B5 and B6 of the second flow control solenoid valve 22 can push the second shift cylinder 52 through the second shift position switch valve 42 to perform a shift operation, or push the fourth shift cylinder 54 through the fourth shift position switch valve 44 to perform a shift operation. Specifically, the second flow control solenoid valve 22 is switchable between a first operating position, in which the inlet A4 of the second flow control solenoid valve 22 communicates with one of the two outlets B5, B6 of the second flow control solenoid valve 22, and a second operating position, in which the second flow control solenoid valve 22 is in the first operating position; when the second flow control solenoid valve 22 is in the second operating position, the inlet A4 of the second flow control solenoid valve 22 communicates with the other of the two outlets B5, B6 of the second flow control solenoid valve 22. In the present embodiment, when the second flow control solenoid valve 22 is in the first operating position (right position as shown in fig. 1), the inlet A4 of the second flow control solenoid valve 22 communicates with the first outlet B5 of the second flow control solenoid valve 22; when the second flow control solenoid valve 22 is switched to the second operating position (the left position as viewed in fig. 1), the inlet A4 of the second flow control solenoid valve 22 communicates with the second outlet B6 of the second flow control solenoid valve 22. That is, by changing the operating position of the second flow control solenoid valve 22, it is possible to selectively direct the pressure oil from the inlet A4 to one of the two outlets B5, B6.

At present, most technical schemes for realizing hydraulic gear shifting control mainly adopt pressure control, and the moving speed of a gear shifting actuating mechanism (namely a gear shifting oil cylinder) cannot be accurately controlled so as to realize accurate control in the gear shifting process. In order to make the hydraulic system control the gear shifting process more accurately based on the gear shifting control, in this embodiment, the second flow control electromagnetic valve 22 is a spool type flow control proportional electromagnetic valve. Therefore, when the second flow control electromagnetic valve 22 is in operation, the spool of the second flow control electromagnetic valve 22 can regulate and control the output flow of the two outlets B5 and B6 to a certain extent under the combined action of the electromagnetic force and the spring load force. That is, the second flow control electromagnetic valve 22 can change the valve opening of the second flow control electromagnetic valve 22 at the current working position by adjusting the current value input to the electromagnet of the second flow control electromagnetic valve 22 at each working position (left or right), so as to adjust the output flow of the two outlets B5 and B6 of the second flow control electromagnetic valve 22, and further control the movement rate of the shift cylinder, so as to realize the accurate control of the shift process.

The first switching solenoid valve 31 has an inlet A5 and an outlet B7, and the second switching solenoid valve 32 has an inlet A6 and an outlet B8. The first gear switching valve 41 has two inlets A7, A8, two outlets B9, B10 and one control end C1. The second position switching valve 42 has two inlets A9, a10, two outlets B11, B12 and one control end C2. The third position switching valve 43 has two inlets a11, a12, two outlets B13, B14 and one control end C3. The fourth gear switching valve 44 has two inlets a13, a14, two outlets B15, B16 and one control terminal C4.

The inlet A5 of the first switching solenoid valve 31 is connected to the main oil passage 10, and the outlet B7 of the first switching solenoid valve 31 is connected to both the control terminal C1 of the first-gear switching valve 41 and the control terminal C2 of the second-gear switching valve 42. The inlet A6 of the second switching solenoid valve 32 is connected to the main oil passage 10, and the outlet B8 of the second switching solenoid valve 32 is connected to both the control terminal C3 of the third-stage switching valve 43 and the control terminal C4 of the fourth-stage switching valve 44.

The two inlets A7, A8 of the first position switching valve 41 are connected to the two outlets B3, B4 of the first flow rate control solenoid valve 21, respectively. The two inlets A9, a10 of the second position switching valve 42 are connected to the two outlets B5, B6 of the second flow rate control solenoid valve 22, respectively. The two inlets a11, a12 of the third position switching valve 43 are connected to the two outlets B3, B4 of the first flow rate control solenoid valve 21, respectively. The two inlets a13, a14 of the fourth-gear switching valve 44 are connected to the two outlets B5, B6 of the second flow rate control solenoid valve 22, respectively.

The two outlets B9, B10 of the first shift switch valve 41 are connected to the two oil chambers of the first shift cylinder 51, respectively. The two outlets B11, B12 of the second shift switch valve 42 are connected to two oil chambers of the second shift cylinder 52, respectively. The two outlets B13, B14 of the third shift switch valve 43 are connected to the two oil chambers of the third shift cylinder 53, respectively. The two outlets B15, B16 of the fourth shift switching valve 44 are connected to the two oil chambers of the fourth shift cylinder 54, respectively.

The first switching solenoid valve 31 is switchable between a cut-off operating position and a cut-on operating position, when the first switching solenoid valve 31 is in the cut-off operating position (right position as shown in fig. 1), the inlet A5 of the first switching solenoid valve 31 is disconnected from the outlet B7 of the first switching solenoid valve 31; when the first switching solenoid valve 31 is in the conducting operating position (the left position as shown in fig. 1), the inlet A5 of the first switching solenoid valve 31 is communicated with the outlet B7 of the first switching solenoid valve 31, and at this time, the pressure oil from the main oil passage 10 is applied to the control end C1 of the first-gear switching valve 41 and the control end C2 of the second-gear switching valve 42 through the first switching solenoid valve 31, so as to push the first-gear switching valve 41 and the second-gear switching valve 42 to perform the reversing operation.

The second on-off solenoid valve 32 is switchable between an off operating position and an on operating position, and when the second on-off solenoid valve 32 is in the off operating position (right position as shown in fig. 1), the inlet A6 of the second on-off solenoid valve 32 is disconnected from the outlet B8 of the second on-off solenoid valve 32; when the second switching solenoid valve 32 is in the conducting operating position (left position as shown in fig. 1), the inlet A6 of the second switching solenoid valve 32 is communicated with the outlet B8 of the second switching solenoid valve 32, and at this time, the pressure oil from the main oil passage 10 is applied to the control end C3 of the third-gear switching valve 43 and the control end C4 of the fourth-gear switching valve 44 via the second switching solenoid valve 32 to push the third-gear switching valve 43 and the fourth-gear switching valve 44 to perform the reversing operation.

In the present embodiment, the first-gear switching valve 41 is a pilot operated directional control valve of a spool type. The first gear switch valve 41 can be switched between a first working position and a second working position, when the first gear switch valve 41 is in the first working position (right position as shown in fig. 1), two inlets A7 and A8 of the first gear switch valve 41 are respectively disconnected with two outlets B9 and B10 of the first gear switch valve 41, and at this time, two outlets B9 and B10 of the first gear switch valve 41 are both communicated to the oil tank; when the first switching solenoid valve 31 is in the conducting operating position and the pressure oil from the main oil path 10 is applied to the control end C1 of the first gear switch valve 41 through the first switching solenoid valve 31 to push the first gear switch valve 41 to switch to the second operating position (the left position as shown in fig. 1), the two inlets A7, A8 of the first gear switch valve 41 are respectively communicated with the two outlets B9, B10 of the first gear switch valve 41, and at this time, the pressure oil from the first flow control solenoid valve 21 can enter the first shift cylinder 51 through the first gear switch valve 41 to push the first shift cylinder 51 to perform the shifting operation.

In this embodiment, the second-gear switching valve 42 is a pilot operated directional control valve of a spool type. The second-gear switch valve 42 is switchable between a first working position and a second working position, when the second-gear switch valve 42 is in the first working position (right position as shown in fig. 1), two inlets A9, a10 of the second-gear switch valve 42 are respectively disconnected from two outlets B11, B12 of the second-gear switch valve 42, and at this time, two outlets B11, B12 of the second-gear switch valve 42 are both communicated to the oil tank; when the first switching solenoid valve 31 is in the conducting operating position, and the pressure oil from the main oil path 10 is applied to the control end C2 of the second position switch valve 42 through the first switching solenoid valve 31 to push the second position switch valve 42 to switch to the second operating position (the left position as shown in fig. 1), the two inlets A9, a10 of the second position switch valve 42 are respectively communicated with the two outlets B11, B12 of the second position switch valve 42, and at this time, the pressure oil from the second flow control solenoid valve 22 can enter the second shift cylinder 52 through the second position switch valve 42 to push the second shift cylinder 52 to perform a shifting operation.

In this embodiment, the third-gear switching valve 43 is a pilot operated directional control valve of a spool type. The third position switch valve 43 can be switched between a first working position and a second working position, when the third position switch valve 43 is in the first working position (right position as shown in fig. 1), two inlets a11 and a12 of the third position switch valve 43 are respectively disconnected with two outlets B13 and B14 of the third position switch valve 43, and at the moment, two outlets B13 and B14 of the third position switch valve 43 are both communicated with the oil tank; when the second switching solenoid valve 32 is in the conducting operating position and the pressure oil from the main oil passage 10 is applied to the control end C3 of the third position switch valve 43 through the second switching solenoid valve 32 to push the third position switch valve 43 to switch to the second operating position (the left position as shown in fig. 1), the two inlets a11, a12 of the third position switch valve 43 are respectively communicated with the two outlets B13, B14 of the third position switch valve 43, and at this time, the pressure oil from the first flow control solenoid valve 21 can enter the third shift cylinder 53 through the third position switch valve 43 to push the third shift cylinder 53 to perform a shifting operation.

In the present embodiment, the fourth-gear switching valve 44 is a pilot operated directional control valve of a spool type. The fourth gear switching valve 44 is switchable between a first operating position and a second operating position, when the fourth gear switching valve 44 is in the first operating position (right position as shown in fig. 1), two inlets a13, a14 of the fourth gear switching valve 44 are respectively disconnected from two outlets B15, B16 of the fourth gear switching valve 44, and at this time, two outlets B15, B16 of the fourth gear switching valve 44 are both communicated to the oil tank; when the second on-off solenoid valve 32 is in the conducting operating position and the pressure oil from the main oil passage 10 is applied to the control end C4 of the fourth position switch valve 44 via the second on-off solenoid valve 32 to push the fourth position switch valve 44 to switch to the second operating position (the left position as shown in fig. 1), the two inlets a13, a14 of the fourth position switch valve 44 are respectively communicated with the two outlets B15, B16 of the fourth position switch valve 44, and at this time, the pressure oil from the second flow control solenoid valve 22 can enter the fourth shift cylinder 54 through the fourth position switch valve 44 to push the fourth shift cylinder 54 to perform the shifting operation.

As described above, the outlet of the first pressure control solenoid valve 11 is connected to the inlet of the first flow control solenoid valve 21, the outlet of the second pressure control solenoid valve 12 is connected to the inlet of the second flow control solenoid valve 22, the outlet of the first flow control solenoid valve 21 is connected to the inlet of the first shift switching valve 41 and the inlet of the third shift switching valve 43, the outlet of the second flow control solenoid valve 22 is connected to the inlet of the second shift switching valve 42 and the inlet of the fourth shift switching valve 44, the outlet of the first shift switching valve 41 is connected to the oil chamber of the first shift cylinder 51, the outlet of the second shift switching valve 42 is connected to the oil chamber of the second shift cylinder 52, the outlet of the third shift switching valve 43 is connected to the oil chamber of the third shift cylinder 53, the outlet of the fourth shift switching valve 44 is connected to the oil chamber of the fourth shift cylinder 54, the outlet of the first switching solenoid valve 31 is connected to the control terminal of the first shift switching valve 41 and the control terminal of the second shift switching valve 42, the first and second switching valve 41 and the second switching valve 42 are connected by the first switching valve 42, the second switching valve 32 and the inlet of the second switching valve 32, the second switching valve 32 and the second switching valve 32 are connected to the inlet of the second switching valve 32, and the second switching valve 32, the outlet of the second switching valve 32 are connected by the first switching valve 32, and the second switching valve 32.

The first pressure control solenoid valve 11 can adjust the inlet pressure of the first flow control solenoid valve 21, the first flow control solenoid valve 21 can accurately control the pressure and flow of the outlet according to the inlet pressure, and the first flow control solenoid valve 21 can also perform reversing control of an oil path to change a pressure oil port and an oil drain port. The second pressure control solenoid valve 12 can adjust the inlet pressure of the second flow control solenoid valve 22, the second flow control solenoid valve 22 can accurately control the outlet pressure and flow according to the inlet pressure, and the second flow control solenoid valve 22 can also perform the reversing control of the oil path to change the pressure oil port and the oil drain port. The first switching solenoid valve 31 may control opening and closing of the first and second position switching valves 41 and 42, and the second switching solenoid valve 32 may control opening and closing of the third and fourth position switching valves 43 and 44, so that the first and third shift cylinders 51 and 53 are connected to the pressure port and the drain port of the first flow control solenoid valve 21, and the second and fourth shift cylinders 52 and 54 are connected to the pressure port and the drain port of the second flow control solenoid valve 22.

Therefore, by controlling the first pressure control solenoid valve 11, the first flow control solenoid valve 21, and the first switching solenoid valve 31, the first shift cylinder 51 can be caused to move at a certain rate between the first position and the second position. Assuming that the first shift cylinder 51 is used to control reverse gear and 6 th gear in the present embodiment, when the first pressure control solenoid valve 11 and the first switching solenoid valve 31 are turned on and the first flow control solenoid valve 21 is in the first operating position (right position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the first outlet B3 of the first flow control solenoid valve 21 after pressure and flow regulation by the first pressure control solenoid valve 11 and the first flow control solenoid valve 21, and since the first shift switch valve 41 has been switched to the on position under the control of the first switching solenoid valve 31, the pressure oil in the first outlet B3 of the first flow control solenoid valve 21 will reach the first outlet B9 through the first inlet A7 of the first shift switch valve 41 and then reach the left chamber of the first shift cylinder 51, pushing the first shift cylinder 51 to move right and engage 6 th gear; when the first pressure control solenoid valve 11 and the first switching solenoid valve 31 are conducted and the first flow control solenoid valve 21 is in the second working position (left position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the second outlet B4 of the first flow control solenoid valve 21 after being subjected to pressure and flow regulation by the first pressure control solenoid valve 11 and the first flow control solenoid valve 21, and since the first shift switching valve 41 has been switched to the conducting position under the control of the first switching solenoid valve 31, the pressure oil in the second outlet B4 of the first flow control solenoid valve 21 will reach the second outlet B10 through the second inlet A8 of the first shift switching valve 41 and then reach the right chamber of the first shift cylinder 51, pushing the first shift cylinder 51 to move left and putting into reverse gear.

By controlling the second pressure control solenoid valve 12, the second flow control solenoid valve 22, and the first switching solenoid valve 31, the second shift cylinder 52 can be moved at a certain rate between the first position and the second position. Assuming that the second shift cylinder 52 is used to control the 7 th gear and the 3 rd gear in the present embodiment, when the second pressure control solenoid valve 12 and the first switching solenoid valve 31 are turned on and the second flow control solenoid valve 22 is in the first operating position (right position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the first outlet B5 of the second flow control solenoid valve 22 after pressure and flow adjustment is performed by the second pressure control solenoid valve 12 and the second flow control solenoid valve 22, and since the second shift switch valve 42 has been switched to the on position under the control of the first switching solenoid valve 31, the pressure oil in the first outlet B5 of the second flow control solenoid valve 22 will reach the first outlet B11 through the first inlet A9 of the second shift switch valve 42 and then reach the left chamber of the second shift cylinder 52, pushing the second shift cylinder 52 to move to the right and engage the 3 rd gear; when the second pressure control solenoid valve 12 and the first switching solenoid valve 31 are turned on and the second flow control solenoid valve 22 is in the second operating position (left position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the second outlet B6 of the second flow control solenoid valve 22 after being subjected to pressure and flow regulation by the second pressure control solenoid valve 12 and the second flow control solenoid valve 22, and since the second shift switching valve 42 has been switched to the on position under the control of the first switching solenoid valve 31, the pressure oil in the second outlet B6 of the second flow control solenoid valve 22 will reach the second outlet B12 through the second inlet a10 of the second shift switching valve 42 and then reach the right chamber of the second shift cylinder 52, pushing the second shift cylinder 52 to the left and engaging 7 th gear.

The third shift cylinder 53 can be moved at a certain rate between the first position and the second position by controlling the first pressure control solenoid valve 11, the first flow rate control solenoid valve 21, and the second switching solenoid valve 32. Assuming that the third shift cylinder 53 is used to control the 5 th gear and the 1 st gear, when the first pressure control solenoid valve 11 and the second switching solenoid valve 32 are turned on and the first flow control solenoid valve 21 is in the first operating position (right position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the first outlet B3 of the first flow control solenoid valve 21 after being subjected to pressure and flow regulation by the first pressure control solenoid valve 11 and the first flow control solenoid valve 21, and since the third shift switch valve 43 has been switched to the on position under the control of the second switching solenoid valve 32, the pressure oil in the first outlet B3 of the first flow control solenoid valve 21 will reach the first outlet B13 by the first inlet a11 of the third shift switch valve 43 and then reach the left chamber of the third shift cylinder 53, pushing the third shift cylinder 53 to the right and engaging the 1 st gear; when the first pressure control solenoid valve 11 and the second switching solenoid valve 32 are turned on and the first flow control solenoid valve 21 is in the second operating position (left position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the second outlet B4 of the first flow control solenoid valve 21 after being subjected to pressure and flow regulation by the first pressure control solenoid valve 11 and the first flow control solenoid valve 21, and since the third position switching valve 43 has been switched to the on position under the control of the second switching solenoid valve 32, the pressure oil in the second outlet B4 of the first flow control solenoid valve 21 will reach the second outlet B14 through the second inlet a12 of the third position switching valve 43 and then reach the right chamber of the third shift cylinder 53, pushing the third shift cylinder 53 to the left and engaging 5 th gear.

By controlling the second pressure control solenoid valve 12, the second flow control solenoid valve 22, and the second on-off solenoid valve 32, the fourth shift cylinder 54 can be caused to move at a rate between the first position and the second position. Assuming that the fourth shift cylinder 54 is used to control the 4 th gear and the 2 nd gear in the present embodiment, when the second pressure control solenoid valve 12 and the second switching solenoid valve 32 are turned on and the second flow control solenoid valve 22 is in the first operating position (right position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the first outlet B5 of the second flow control solenoid valve 22 after pressure and flow adjustment is performed by the second pressure control solenoid valve 12 and the second flow control solenoid valve 22, and since the fourth shift switch valve 44 is switched to the on position under the control of the second switching solenoid valve 32, the pressure oil in the first outlet B5 of the second flow control solenoid valve 22 will reach the first outlet B15 through the first inlet a13 of the fourth shift switch valve 44 and then reach the left chamber of the fourth shift cylinder 54, pushing the fourth shift cylinder 54 to move to the right and engage the 2 nd gear; when the second pressure control solenoid valve 12 and the second switching solenoid valve 32 are turned on and the second flow control solenoid valve 22 is in the second operating position (left position as shown in fig. 1), the pressure oil from the main oil passage 10 reaches the second outlet B6 of the second flow control solenoid valve 22 after being subjected to pressure and flow regulation by the second pressure control solenoid valve 12 and the second flow control solenoid valve 22, and since the fourth shift switching valve 44 has been switched to the on position under the control of the second switching solenoid valve 32, the pressure oil in the second outlet B6 of the second flow control solenoid valve 22 will reach the second outlet B16 through the second inlet a14 of the fourth shift switching valve 44 and then reach the right chamber of the fourth shift cylinder 54, pushing the fourth shift cylinder 54 to the left and putting up 4 th shift.

Therefore, in the embodiment of the invention, the gear shifting control of the automatic transmission with eight gears is realized by adopting the combination of the electromagnetic valves and the slide valves as few as possible, and the double control of the gear shifting pressure and the gear shifting flow is realized on the basis of realizing the gear shifting control of the transmission through the two pressure control electromagnetic valves 11 and 12 and the two flow control electromagnetic valves 21 and 22, so that the hydraulic system can control the gear shifting process more accurately, and the accurate control of the gear shifting process can be better realized.

In addition, based on the operating characteristics of the dual clutch automatic transmission, there may be situations where both odd and even gears are engaged at the same time (e.g., when a certain odd gear is currently engaged, a next even gear may be pre-engaged, or when a certain even gear is currently engaged, a next odd gear may be pre-engaged), but the simultaneous engagement of multiple odd gears or the simultaneous engagement of multiple even gears is not allowed at the same time. In this embodiment, the reverse gear and the 6 th gear are controlled by three solenoid valves, i.e., the first pressure control solenoid valve 11, the first flow control solenoid valve 21 and the first switching solenoid valve 31, and the 4 th gear and the 2 nd gear are controlled by three solenoid valves, i.e., the second pressure control solenoid valve 12, the second flow control solenoid valve 22 and the second switching solenoid valve 32, so that it can be seen that the three solenoid valves controlling the reverse gear and the 6 th gear are all different from the three solenoid valves controlling the 4 th gear and the 2 nd gear, and therefore, the possibility of engaging a plurality of even-numbered gears is greatly reduced; in addition, the 7 th and 3 rd gears are controlled by three solenoid valves of the second pressure control solenoid valve 12, the second flow control solenoid valve 22 and the first switching solenoid valve 31, and the 5 th and 1 st gears are controlled by three solenoid valves of the first pressure control solenoid valve 11, the first flow control solenoid valve 21 and the second switching solenoid valve 32, and thus it can be seen that the three solenoid valves controlling the 7 th and 3 rd gears are different from the three solenoid valves controlling the 5 th and 1 st gears, and thus the possibility of simultaneously engaging a plurality of odd-numbered gears is greatly reduced. Therefore, the present embodiment also improves safety in preventing erroneous engagement.

The hydraulic shift control system of the present embodiment further includes a main pump 61, a sub-pump 62, and an oil tank 63. The main pump 61 and the sub pump 62 draw oil from an oil tank 63 via an oil suction filter 64, thereby supplying pressure oil required for operation to the main oil passage 10 of the hydraulic shift control system. In the present embodiment, the main pump 61 is directly driven by the engine of the automobile, the sub-pump 62 is driven by the motor, and the sub-pump 62 can assist the main pump 61 when the oil delivery amount of the main pump 61 is insufficient, on the one hand, and can ensure the supply of the pressure oil in the system when the engine and therefore the main pump 61 are stopped, on the other hand. Tank symbols are used at various locations in fig. 1, and are understood to be communicated to the tank 63 via associated lines.

To prevent the reverse flow of the oil, check valves 65 are connected to outlets of the main pump 61 and the sub pump 62. In order to control the maximum pressure in the system, a system safety valve 66 is further connected to the outlet of the main pump 61, and the system safety valve 66 may be a safety relief valve or a check valve, in this embodiment, the system safety valve 66 is a check valve and is connected between the outlet of the main pump 61 and the oil tank 63, the maximum pressure allowed in the system is set through the check valve, and when the pressure in the system exceeds the maximum pressure, the check valve is opened to drain oil.

The hydraulic shift control system of the present embodiment 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 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 B17, the inlet a15 of the first clutch solenoid valve 71 is connected to the main oil passage 10, and the outlet B17 of the first clutch solenoid valve 71 is connected to the clutch relief valve 73. The first clutch solenoid valve 71 is switchable between a cut-off operating position and a cut-on operating position, and when the first clutch solenoid valve 71 is in the cut-off operating position (right position as shown in fig. 1), the inlet a15 of the first clutch solenoid valve 71 is disconnected from the outlet B17 of the first clutch solenoid valve 71, and the outlet B17 of the first clutch solenoid valve 71 is communicated to the oil tank 63, at which time the first clutch T1 is disengaged; when the first clutch solenoid valve 71 is in the conducting operating position (left position as viewed in fig. 1), the inlet a15 of the first clutch solenoid valve 71 communicates with the outlet B17 of the first clutch solenoid valve 71, and at this time, the pressure oil from the main oil passage 10 drives the first clutch T1 to engage via the first clutch solenoid valve 71 and the clutch relief valve 73.

The second clutch solenoid valve 72 is used to control the engagement or disengagement of the second clutch T2. The second clutch solenoid valve 72 has an inlet a16 and an outlet B18, the inlet a16 of the second clutch solenoid valve 72 is connected to the main oil passage 10, and the outlet B18 of the second clutch solenoid valve 72 is connected to the clutch relief valve 73. The second clutch solenoid valve 72 is switchable between a cut-off operating position and a cut-on operating position, when the second clutch solenoid valve 72 is in the cut-off operating position (right position as shown in fig. 1), the inlet a16 of the second clutch solenoid valve 72 is disconnected from the outlet B18 of the second clutch solenoid valve 72, and the outlet B18 of the second clutch solenoid valve 72 is connected to the oil tank 63, at which time the second clutch T2 is disconnected; when the second clutch solenoid valve 72 is in the conducting operating position (left position as shown in fig. 1), the inlet a16 of the second clutch solenoid valve 72 communicates with the outlet B18 of the second clutch solenoid valve 72, and at this time, the pressure oil from the main oil passage 10 drives the second clutch T2 to engage via the second clutch solenoid valve 72 and the clutch relief valve 73.

The clutch relief valve 73 is configured to cut off the oil passage to the clutches T1, T2 when the clutches T1, T2 fail. The clutch relief valve 73 has two inlets a17, a18, two outlets B19, B20 and a control terminal C5, the two inlets a17, a18 of the clutch relief valve 73 are connected to the outlet B17 of the first clutch solenoid valve 71 and the outlet B18 of the second clutch solenoid valve 72, respectively, the two outlets B19, B20 of the clutch relief valve 73 are connected to the first clutch T1 and the second clutch T2, respectively, and the outlet B7 of the first switching solenoid valve 31 and the outlet B8 of the second switching solenoid valve 32 are connected to the control terminal C5 of the clutch relief valve 73 at the same time. The clutch relief valve 73 is switchable between an open position and a closed position, and when the clutch relief valve 73 is in the open position (left position as shown in fig. 1), the two inlets a17, a18 of the clutch relief valve 73 are respectively communicated with the two outlets B19, B20 of the clutch relief valve 73, 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 the engagement or disengagement of the second clutch T2 can be realized by controlling the reversing operation of the second clutch solenoid valve 72; when the clutches T1 and T2 are out of order, the first switching solenoid valve 31 and the second switching solenoid valve 32 are opened simultaneously, so that the pressure oil output by the first switching solenoid valve 31 and the second switching solenoid valve 32 is simultaneously applied to the control end C5 of the clutch relief valve 73, and the clutch relief valve 73 is pushed to switch from the open position to the closed position (the right position as shown in fig. 1), at this time, the two inlets a17 and a18 of the clutch relief valve 73 are respectively disconnected from the two outlets B19 and B20 of the clutch relief valve 73, so that the oil passages to the clutches T1 and T2 are cut off, and at this time, the first clutch T1 and the second clutch T2 are unloaded by the clutch relief valve 73.

The hydraulic shift control system of the present embodiment further includes a third switching solenoid valve 33, a parking control valve 81, and a parking cylinder 82. The third switching solenoid valve 33 has an inlet a19 and an outlet B21. An inlet a19 of the third switching solenoid valve 33 is connected to the main oil passage 10, and an outlet B21 of the third switching solenoid valve 33 is connected to a control port C6 of the parking control valve 81. The third switching solenoid valve 33 is switchable between a cut-off operating position and a conducting operating position, and when the third switching solenoid valve 33 is in the cut-off operating position (right position as shown in fig. 1), the inlet a19 of the third switching solenoid valve 33 is disconnected from the outlet B21 of the third switching solenoid valve 33; when the third switching solenoid valve 33 is in the on operating position (left position as viewed in fig. 1), the inlet a19 of the third switching solenoid valve 33 communicates with the outlet B21 of the third switching solenoid valve 33, and at this time, the pressure oil from the main oil passage 10 is applied to the control port C6 of the parking control valve 81 via the third switching solenoid valve 33 to push the parking control valve 81 to reverse.

In this embodiment, the parking control valve 81 is a slide valve type pilot operated directional control valve. The parking control valve 81 has an inlet a20, two outlets B22, B23, and a control end C6, the inlet a20 of the parking control valve 81 is connected to the main oil passage 10, the two outlets B22, B23 of the parking control valve 81 are respectively connected to the two oil chambers of the parking cylinder 82, and the control end C6 of the parking control valve 81 is connected to the outlet B21 of the third switching solenoid valve 33. The parking control valve 81 is switchable between a first operating position and a second operating position, when the parking control valve 81 is in the first operating position (right position as shown in fig. 1), the inlet a20 of the parking control valve 81 is communicated with the first outlet B22 of the parking control valve 81, the second outlet B23 of the parking control valve 81 is communicated with the oil tank 63, and at this time, the pressure oil from the main oil passage 10 passes through the parking control valve 81 and enters one of the oil chambers of the parking cylinder 82 to push the parking cylinder 82 to move to one side; when the third on/off solenoid valve 33 is in the on position, and the pressure oil from the main oil passage 10 is applied to the control end C6 of the parking control valve 81 through the third on/off solenoid valve 33 to push the parking control valve 81 to be switched to the second position (the left position as shown in fig. 1), the inlet a20 of the parking control valve 81 is communicated with the second outlet B23 of the parking control valve 81, the first outlet B22 of the parking control valve 81 is communicated with the oil tank 63, and the pressure oil from the main oil passage 10 enters another oil chamber of the parking cylinder 82 through the parking control valve 81 to push the parking cylinder 82 to move to the other side. Thus, the automatic parking and unlocking functions of the vehicle are realized through the third switching solenoid valve 33, the parking control valve 81, and the parking cylinder 82.

The hydraulic shift control system of the present embodiment further includes a third pressure control solenoid valve 13 and a main oil passage pressure regulating valve 18.

The third pressure control solenoid valve 13 has an inlet a21 and an outlet B24. The main oil-pressure regulating valve 18 has an inlet a22, two outlets B25, B26 (or referred to as a first outlet B25 and a second outlet B26), and two control ends C7, C8 (or referred to as a first control end C7 and a second control end C8). The inlet a21 of the third pressure control solenoid valve 13 is connected to the main oil passage 10, the outlet B24 of the third pressure control solenoid valve 13 is connected to the first control end C7 of the main oil passage pressure regulating valve 18, the inlet a22 and the second control end C8 of the main oil passage pressure regulating valve 18 are simultaneously connected to the main oil passage 10, the first outlet B25 of the main oil passage pressure regulating valve 18 is connected to the oil tank 63, and the second outlet B26 of the main oil passage pressure regulating valve 18 is opened to a lubricating and cooling oil passage for lubricating and cooling related elements (such as bearings, gears, clutches, etc.).

In the present embodiment, the third pressure control solenoid valve 13 is a spool type pressure control proportional solenoid valve, and the pressure at the outlet B24 of the third pressure control solenoid valve 13 is fed back to one end of the third pressure control solenoid valve 13 (fed back to the solenoid end in fig. 1) through an oil passage. Therefore, when the third pressure control solenoid valve 13 is operated, the spool of the third pressure control solenoid valve 13 can adjust and control the output pressure of the outlet B24 under the combined action of the electromagnetic force, the spring load force and the hydraulic feedback force, so as to change the acting force applied to the first control end C7 of the main oil path pressure regulating valve 18, and gradually switch the main oil path pressure regulating valve 18 from the closed position to the open position, thereby adjusting the oil pressure in the main oil path 10, and simultaneously, the redundant oil in the main oil path 10 can be delivered to the lubricating and cooling oil path through the main oil path pressure regulating valve 18, so as to meet the requirements of oil cooling and lubrication of related elements.

In the present embodiment, the main oil passage pressure regulating valve 18 has three operating positions. When the output pressure at the outlet B24 of the third pressure control solenoid valve 13 is greater, the force acting on the first control end C7 of the main oil passage pressure regulating valve 18 is also greater, and at this time, the main oil passage pressure regulating valve 18 is in the first operating position (the right position as viewed in fig. 1), and the inlet a22 of the main oil passage pressure regulating valve 18 is disconnected from both outlets B25, B26 of the main oil passage pressure regulating valve 18; as the output pressure at the outlet B24 of the third pressure control solenoid valve 13 decreases, the force acting on the first control end C7 of the main oil passage pressure regulating valve 18 also decreases, and the force acting on the second control end C8 of the main oil passage pressure regulating valve 18 at this time is greater than the force acting on the first control end C7, so as to urge the main oil passage pressure regulating valve 18 to switch to the second operating position (the neutral position shown in fig. 1), and the inlet a22 of the main oil passage pressure regulating valve 18 communicates with the second outlet B26 of the main oil passage pressure regulating valve 18, so that the oil can be led to the lubricating and cooling oil passage via the main oil passage pressure regulating valve 18; as the output pressure at the outlet B24 of the third pressure control solenoid valve 13 continues to decrease, the main line pressure regulating valve 18 will switch to a third operating position (left position as viewed in fig. 1), in which the inlet a22 of the main line pressure regulating valve 18 is in communication with both outlets B25, B26 of the main line pressure regulating valve 18, a portion of the oil may be directed to the lubricating cooling line via the main line pressure regulating valve 18, and another portion of the oil may be returned to the tank 63 via the main line pressure regulating valve 18.

The hydraulic shift control system of the present embodiment further includes a fourth pressure control solenoid valve 14. The fourth pressure control solenoid valve 14 has an inlet a23 and an outlet B27. An inlet a23 of the fourth pressure control solenoid valve 14 is connected to the main oil passage 10, and an outlet B27 of the fourth pressure control solenoid valve 14 is connected to the lubricating-cooling oil passage.

In the present embodiment, the fourth pressure control solenoid valve 14 is a spool-type pressure control proportional solenoid valve, and the pressure at the outlet B27 of the fourth pressure control solenoid valve 14 is fed back to one end of the fourth pressure control solenoid valve 14 (fed back to the solenoid end as shown in fig. 1) through an oil passage. Therefore, when the fourth pressure control solenoid valve 14 is in operation, the spool of the fourth pressure control solenoid valve 14 can regulate and control the output pressure of the outlet B27 under the combined action of the electromagnetic force, the spring load force, and the hydraulic feedback force.

[ second embodiment ]

Fig. 2 is a schematic structural diagram of a hydraulic shift control system of a dual clutch automatic transmission according to a second embodiment of the present invention, which is different from the first embodiment in that in the present embodiment, a first switching solenoid valve 31 and a second switching solenoid valve 32 are integrated into a three-position four-way switching solenoid valve 34, an inlet A5 of the first switching solenoid valve 31 and an inlet A6 of the second switching solenoid valve 32 are integrated into one inlet a24 of the three-position four-way switching solenoid valve 34 and are connected to the main oil passage 10, and an outlet B7 of the first switching solenoid valve 31 and an outlet B8 of the second switching solenoid valve 32 are two outlets of the three-position four-way switching solenoid valve 34, respectively.

The three-position four-way switching solenoid valve 34 can be switched among a cut-off position, a first working position and a second working position, in the embodiment, when the switching solenoid valve 34 is located at the cut-off position (as shown in the middle position of fig. 2), the inlet a24 of the switching solenoid valve 34 is disconnected and not communicated with the first outlet B7 and the second outlet B8 of the switching solenoid valve 34, and at the moment, the first outlet B7 and the second outlet B8 of the switching solenoid valve 34 are communicated to the oil tank; when the on-off solenoid valve 34 is switched to the first working position (the right position shown in fig. 2), the inlet a24 of the on-off solenoid valve 34 is communicated with the first outlet B7 of the on-off solenoid valve 34, and the second outlet B8 of the on-off solenoid valve 34 is communicated to the oil tank; when the on-off solenoid valve 34 is switched to the second operating position (the left position as shown in fig. 2), the inlet a24 of the on-off solenoid valve 34 communicates with the second outlet B8 of the on-off solenoid valve 34, and the first outlet B7 of the on-off solenoid valve 34 communicates with the tank. That is, by changing the operation position of the on-off solenoid valve 34, it is possible to selectively guide the pressure oil from the inlet a24 to one of the two outlets B7, B8, and thus it is possible to integrate the first on-off solenoid valve 31 and the second on-off solenoid valve 32 in the above-described first embodiment into one on-off solenoid valve, further reducing the number of spool valves and reducing the cost.

In addition, the present embodiment is also different from the above-described first embodiment in that, in the above-described first embodiment, the outlet B7 of the first switching solenoid valve 31 and the outlet B8 of the second switching solenoid valve 32 are simultaneously connected to the control end C5 of the clutch relief valve 73. In the present embodiment, the outlet B1 of the first pressure control solenoid valve 11 and the outlet B2 of the second pressure control solenoid valve 12 are connected to the control end C2 of the clutch relief valve 73 at the same time, so that when the clutches T1, T2 are out of order, the first pressure control solenoid valve 11 and the second pressure control solenoid valve 12 are opened at the same time, so that the pressure oil output from the first pressure control solenoid valve 11 and the second pressure control solenoid valve 12 is applied to the control end C5 of the clutch relief valve 73 at the same time, so as to jointly push the clutch relief valve 73 to perform reversal.

Other structures and working principles of this embodiment can be referred to the first embodiment, and are not described herein again.

Although the present invention has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims (8)

1. A hydraulic gear-shifting control system of a double-clutch automatic transmission is characterized by comprising a first pressure control electromagnetic valve (11), a second pressure control electromagnetic valve (12), a first flow control electromagnetic valve (21), a second flow control electromagnetic valve (22), a first switch electromagnetic valve (31), a second switch electromagnetic valve (32), a first gear switch valve (41), a second gear switch valve (42), a third gear switch valve (43), a fourth gear switch valve (44), a first gear shifting oil cylinder (51), a second gear shifting oil cylinder (52), a third gear shifting oil cylinder (53) and a fourth gear shifting oil cylinder (54);

the first pressure control solenoid valve (11) has an inlet (A1) and an outlet (B1), the second pressure control solenoid valve (12) has an inlet (A2) and an outlet (B2), the first flow control solenoid valve (21) has an inlet (A3) and two outlets (B3, B4), the second flow control solenoid valve (22) has an inlet (A4) and two outlets (B5, B6), the inlet (A1) of the first pressure control solenoid valve (11) and the inlet (A2) of the second pressure control solenoid valve (12) are both connected to the main oil line (10), the outlet (B1) of the first pressure control solenoid valve (11) is connected to the inlet (A3) of the first flow control solenoid valve (21), the outlet (B2) of the second pressure control solenoid valve (12) is connected to the inlet (A4) of the second flow control solenoid valve (22), the two outlets (B3, B4) of the first flow control solenoid valve (21) are connected to the first position switch valve (41) and the second switch valve (43, B6) are connected to the second switch valve (42, the second switch (42) and the second switch (6) and the second switch (42);

the first switching solenoid valve (31) has an inlet (A5) and an outlet (B7), the second switching solenoid valve (32) has an inlet (A6) and an outlet (B8), the first gear switching valve (41) has two inlets (A7, A8), two outlets (B9, B10) and a control end (C1), the second gear switching valve (42) has two inlets (A9, A10), two outlets (B11, B12) and a control end (C2), the third gear switching valve (43) has two inlets (A11, A12), two outlets (B13, B14) and a control end (C3), the fourth gear switching valve (44) has two inlets (A13, A14), two outlets (B15, B16) and a control end (C4), an inlet (A5) of the first switch electromagnetic valve (31) and an inlet (A6) of the second switch electromagnetic valve (32) are connected with the main oil way (10), an outlet (B7) of the first switch electromagnetic valve (31) is simultaneously connected with a control end (C1) of the first gear switch valve (41) and a control end (C2) of the second gear switch valve (42), the first gear switch valve (41) and the second gear switch valve (42) are controlled by the first switch electromagnetic valve (31) to be reversed, and an outlet (B8) of the second switch electromagnetic valve (32) is simultaneously connected with the third gear switch electromagnetic valve (32) A control end (C3) of a shut-off valve (43) is connected with a control end (C4) of a fourth gear switch valve (44), the third gear switch valve (43) and the fourth gear switch valve (44) are controlled by the second switch solenoid valve (32) to perform reversing, two inlets (A7, A8) of the first gear switch valve (41) are respectively connected with two outlets (B3, B4) of the first flow control solenoid valve (21), two inlets (A9, A10) of the second gear switch valve (42) are respectively connected with two outlets (B5, B6) of the second flow control solenoid valve (22), two inlets (A11, A12) of the third gear switch valve (43) are respectively connected with two outlets (B3, B4) of the first flow control solenoid valve (21), two inlets (A13, A14) of the fourth gear switch valve (44) are respectively connected with two outlets (B3, B4) of the second flow control solenoid valve (11), two inlets (B14) of the second flow control solenoid valve (21), two inlets (A13, A14) of the fourth gear switch valve (44) are respectively connected with two outlets (B11, B12) of the second switch valve (11) of the second flow control solenoid valve (22), two oil chamber (51) are respectively connected with two outlets (11) of the second oil cylinder (51), two outlets (B15, B16) of the fourth gear switch valve (44) are respectively connected with two oil cavities of the fourth gear shifting cylinder (54).

2. The hydraulic shift control system of a dual clutch automatic transmission as set forth in claim 1, characterized in that the first flow control solenoid valve (21) is switchable between a first operating position and a second operating position, and when the first flow control solenoid valve (21) is in the first operating position, the inlet (A3) of the first flow control solenoid valve (21) communicates with one of the two outlets (B3, B4) of the first flow control solenoid valve (21); when the first flow control electromagnetic valve (21) is in the second working position, the inlet (A3) of the first flow control electromagnetic valve (21) is communicated with the other of the two outlets (B3, B4) of the first flow control electromagnetic valve (21).

3. The hydraulic shift control system of a dual clutch automatic transmission as recited in claim 1, characterized in that the second flow control solenoid valve (22) is switchable between a first operating position and a second operating position, and when the second flow control solenoid valve (22) is in the first operating position, an inlet (A4) of the second flow control solenoid valve (22) communicates with one of two outlets (B5, B6) of the second flow control solenoid valve (22); when the second flow control electromagnetic valve (22) is in the second working position, the inlet (A4) of the second flow control electromagnetic valve (22) is communicated with the other of the two outlets (B5, B6) of the second flow control electromagnetic valve (22).

4. The hydraulic shift control system of a dual clutch automatic transmission according to claim 1, characterized in that the first pressure control solenoid valve (11) and the second pressure control solenoid valve (12) are both slide valve type pressure control proportional solenoid valves, the first flow control solenoid valve (21) and the second flow control solenoid valve (22) are both slide valve type flow control proportional solenoid valves, 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 slide valve type pilot operated directional control valves.

5. A hydraulic shift control system of a dual clutch automatic transmission as claimed in claim 1, 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 (B17), the second clutch solenoid valve (72) having an inlet (A16) and an outlet (B18), 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 (B19, B20) and a control end (C5), the two inlets (A17, A18) of the clutch safety valve (73) are respectively connected with the outlet (B17) of the first clutch solenoid valve (71) and the outlet (B18) of the second clutch solenoid valve (72), the two outlets (B19, B20) of the clutch safety valve (73) are respectively connected with the first clutch (T1) and the second clutch (T2), the outlet (B7) of the first on-off solenoid valve (31) and the outlet (B8) of the second on-off solenoid valve (32) are connected to the control end (C5) of the clutch relief valve (73) at the same time.

6. The hydraulic shift control system of a dual clutch automatic transmission according to claim 1, characterized by further comprising a third switching solenoid valve (33), a parking control valve (81), and a parking cylinder (82), the third switching solenoid valve (33) having an inlet (a 19) and an outlet (B21), the parking control valve (81) having an inlet (a 20), two outlets (B22, B23), and a control end (C6), the inlet (a 19) of the third switching solenoid valve (33) and the inlet (a 20) of the parking control valve (81) both being connected to the main oil passage (10), the outlet (B21) of the third switching solenoid valve (33) being connected to the control end (C6) of the parking control valve (81), the two outlets (B22, B23) of the parking control valve (81) being connected to the two oil chambers of the parking cylinder (82), respectively.

7. The hydraulic shift control system of a dual clutch automatic transmission according to claim 1, characterized in that the first switching solenoid valve (31) and the second switching solenoid valve (32) are integrated into a three-position four-way switching solenoid valve (34), the inlet (A5) of the first switching solenoid valve (31) and the inlet (A6) of the second switching solenoid valve (32) are integrated into one inlet (a 24) of the three-position four-way switching solenoid valve (34) and connected to the main oil passage (10), and the outlet (B7) of the first switching solenoid valve (31) and the outlet (B8) of the second switching solenoid valve (32) are two outlets of the three-position four-way switching solenoid valve (34), respectively.

8. The hydraulic shift control system of a double clutch automatic transmission according to any one of claims 1 to 7, characterized by further comprising a third pressure control solenoid valve (13) and a main oil passage pressure regulating valve (18), the third pressure control solenoid valve (13) having an inlet (a 21) and an outlet (B24), the main oil passage pressure regulating valve (18) having an inlet (a 22), a first outlet (B25), a second outlet (B26), a first control end (C7) and a second control end (C8), the inlet (a 21) of the third pressure control solenoid valve (13) being connected to the main oil passage (10), the outlet (B24) of the third pressure control solenoid valve (13) 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 outlet (B25) of the main oil passage pressure regulating valve (18) being connected to the main oil tank outlet (B63), the main oil passage pressure regulating valve (18) being connected to the cooling oil passage (26).

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