CN217951303U - Compact four-position four-way gear shifting control valve - Google Patents

Abstract

The compact four-position four-way gear shifting control valve comprises a valve sleeve with an opening at one end and a valve core coaxially connected in the valve sleeve in a sliding manner, wherein a first oil discharge port, a first oil control port, an oil inlet and a second oil control port are sequentially arranged on the circumferential side wall of the valve sleeve at intervals along the axial direction; a plurality of baffle rings are fixedly connected to the valve core at intervals in sequence along the axial direction, and the plurality of baffle rings control the communication or disconnection between the adjacent oil ports. This application has the effect that reduces control valve structure length, reduces the control valve assembly degree of difficulty.

Description

Compact four-position four-way gear shifting control valve

Technical Field

The application relates to the technical field of shift control valves, in particular to a compact four-position four-way shift control valve.

Background

The gear shifting control valve in the double-clutch transmission is generally a four-position four-way flow control valve, the four-position four-way flow control valve comprises a valve sleeve and a valve core, and the on-off of each oil way can be controlled by matching the axial movement of an oil inlet, an oil control port and an oil discharge port which are arranged on the circumferential side surface of the valve sleeve with the axial movement of the valve core. The oil circuit between the valve sleeve and the valve core has four on-off matching states, and the gear can be adjusted by adjusting the valve core to use different oil circuit on-off matching states.

To the correlation technique among the above-mentioned, the inventor finds that because the oil inlet, accuse oil mouth and oil drain port all set up in valve barrel circumference side, lead to valve barrel and case overall structure longer, the assembly degree of difficulty of control valve self is very big.

SUMMERY OF THE UTILITY MODEL

In order to reduce control valve structure length, reduce the control valve assembly degree of difficulty, this application provides a compact quadbit four-way control valve of shifting.

The application provides a compact quadbit four-way shift control valve adopts following technical scheme:

a compact four-position four-way gear shifting control valve comprises a valve sleeve with an opening at one end and a valve core coaxially connected in the valve sleeve in a sliding manner, wherein a first oil discharge port, a first oil control port, an oil inlet and a second oil control port are sequentially arranged on the circumferential side wall of the valve sleeve at intervals along the axial direction, the first oil discharge port is positioned on one side, close to the opening, of the valve sleeve, and a second oil discharge port is arranged at one end, far away from the opening, of the valve sleeve; a plurality of baffle rings are fixedly connected to the valve core at intervals in sequence along the axial direction, and the plurality of baffle rings control the communication or disconnection between the adjacent oil ports.

Through adopting above-mentioned technical scheme, the second oil drain port is established at the valve barrel tip, under the prerequisite that can accomplish the four-digit cross valve job requirement, compares original oil inlet, accuse oil port and oil drain port and all sets up the structure in valve barrel circumference side, can shorten the length of valve barrel and case, and actual measurement valve barrel length reduces about 18%, and case length reduces about 20%, and whole control valve length reduces about 12%, makes the control valve assembly degree of difficulty reduce. The lengths of the valve sleeve and the valve core are shortened, and the valve core and the valve sleeve can ensure the machining processing precision more easily. The axial contact length of the valve core and the valve sleeve is reduced, and the lateral force is reduced, so that the hysteresis of the electromagnetic valve is reduced.

Optionally, the valve core is sequentially provided with a first baffle ring, a second baffle ring and a third baffle ring, the diameters of the first baffle ring, the second baffle ring and the third baffle ring are equal to the inner diameter of the valve sleeve, and the first baffle ring moves axially to control the on-off of the first oil control port and oil ways on two sides of the first baffle ring; the second retaining ring axially moves to control the connection and disconnection of the oil inlet and oil ways on two sides of the second retaining ring; and the third retainer ring axially moves to control the on-off of the second oil control port and oil paths on two sides of the third retainer ring.

By adopting the technical scheme, the valve core is moved, so that the three stop rings move to complete the on-off treatment of an oil way in the valve sleeve, the structure of the valve core is simplified, the machining and assembling difficulty of the valve core is reduced, and the material of the valve core is saved.

Optionally, an oil passing groove is formed in the first baffle ring, an oil return groove is formed in the valve sleeve and between the first oil discharge port and the first oil control port, and the width of the oil passing groove is larger than the distance between the oil return groove and the first oil control port; the width of the oil return groove is larger than the distance between the oil passing groove and the end face of one side, close to the first oil discharge port, of the first baffle ring; the distance between the first baffle ring and the second baffle ring is larger than the distance between the first oil control port and the oil inlet; the distance between the second baffle ring and the third baffle ring is larger than the distance between the oil inlet and the second oil inlet.

By adopting the technical scheme, the end face of the first baffle ring close to one side of the opening of the valve sleeve does not need to enter the position of the first oil control port, the first oil discharge port and the first oil control port can be communicated by passing through the oil groove and the oil return groove, the moving distance of the valve core adjusting oil way is shortened, and the lengths of the valve core and the valve sleeve are also shortened.

Optionally, the width of the first baffle ring is greater than the diameter of the first oil control port, and the distance between the inner side wall of the oil return groove close to the first oil control port and the oil inlet is greater than the distance between the inner side wall of the oil passing groove close to the first oil discharge port and the side wall of the second baffle ring close to the first baffle ring.

By adopting the technical scheme, the interference oil way generated by the communication between the oil inlet and the first oil outlet can be prevented when the valve core moves.

Optionally, the width of the second retainer is smaller than the diameter of the oil inlet.

By adopting the technical scheme, the axial contact length of the second retaining ring and the valve sleeve is reduced, and the lateral force of the valve core is reduced, so that the hysteresis of the electromagnetic valve is reduced.

Optionally, the width of the third retainer ring is larger than the diameter of the second oil control opening.

By adopting the technical scheme, the interference oil way generated by the communication of the oil inlet and the second oil outlet can be prevented when the valve core moves.

Optionally, a spring is arranged in one end of the valve sleeve, which is provided with the second oil discharge port, one end of the spring is abutted against the inner wall of the end face of the valve sleeve, and the other end of the spring is abutted against the end part of the valve core; one end of the opening of the valve sleeve is connected with a valve seat, a plunger driven by electromagnetic force is arranged in the valve seat, one end of the plunger is connected with a pin shaft, and one end of the pin shaft penetrates out of the valve seat to be abutted against the valve core.

By adopting the technical scheme, when the plunger is not driven by electromagnetic force, the electromagnetic valve has no current, the spring pushes and fixes the valve core at the opening end of the valve sleeve, the position of the valve core is the first adjusting position, the first oil control port and the second oil control port have no flow output, when the gear shifting is not needed, the electromagnetic valve is not needed to be electrified, and the energy waste of a hydraulic system is reduced.

Optionally, the first oil discharge port, the first oil control port, the oil inlet and the second oil control port are radially communicated with two sides of the valve sleeve.

By adopting the technical scheme, the first oil discharge port, the first oil control port, the oil inlet and the second oil control port can bidirectionally feed and discharge hydraulic oil, so that the reaction speed of the control valve is improved. An assembler can observe the internal condition of the valve sleeve from multiple directions through the oil port, and the assembly difficulty is favorably reduced.

In summary, the present application includes at least one of the following beneficial technical effects:

1. the second oil drain port is formed in the end portion of the valve sleeve, so that the lengths of the valve sleeve and the valve core can be shortened, and the assembly difficulty of the control valve is reduced.

2. The lengths of the valve sleeve and the valve core are shortened, and the valve core and the valve sleeve can ensure the machining processing precision more easily.

3. The axial contact length of the valve core and the valve sleeve is reduced, and the lateral force is reduced, so that the hysteresis of the electromagnetic valve is reduced.

4. The widths of the first retaining ring, the second retaining ring and the third retaining ring are smaller, the lateral force of the valve core is lower, and the hysteresis of the electromagnetic valve is also lower.

Drawings

FIG. 1 is a schematic cross-sectional view of a valve cartridge of an embodiment of the present application in a first adjustment position;

FIG. 2 is an enlarged view of a portion A of FIG. 1;

FIG. 3 is a schematic cross-sectional view of a valve cartridge of an embodiment of the present application in a second adjustment position;

FIG. 4 is a fragmentary schematic view of the valve spool of the embodiment of the present application in a second adjustment position;

FIG. 5 is a schematic cross-sectional view of the valve cartridge of the embodiment of the present application in a third adjustment position;

FIG. 6 is a schematic cross-sectional view of the valve spool of the embodiment of the present application in a fourth adjustment position;

in the figure, 1, valve housing; 11. a first oil discharge port; 12. a first oil control port; 13. an oil inlet; 14. a second oil control port; 15. a second oil drain port; 16. an oil return groove; 2. a valve core; 21. a first retainer ring; 211. an oil passing groove; 22. a second retainer ring; 23. a third retainer ring; 3. a spring; 4. a valve seat; 5. a plunger; 6. a push rod.

Detailed Description

The present application is described in further detail below with reference to fig. 1-6.

The application provides a compact four-position four-way gear shifting control valve, referring to fig. 1 and 2, comprising a valve sleeve 1, a valve core 2, a spring 3, a valve seat 4, a plunger 5 and a push rod 6. One end of the valve sleeve 1 is opened, the other end is provided with an end cover plate, and the valve core 2 is arranged in the valve sleeve 1 in a penetrating way and is connected with the valve sleeve 1 in a sliding way. The valve seat 4 is connected with the opening end of the valve sleeve 1, and a plunger 5 which is driven by electromagnetic force to move axially is arranged in the valve seat 4. One end of the plunger 5 is connected with a push rod 6, and one end of the push rod 6 penetrates through the valve seat 4 to be abutted against the valve core 2. And a spring 3 is arranged between one end of the valve core 2 far away from the valve seat 4 and the end cover plate of the valve sleeve 1 along the axial direction, and the spring 3 is always in a compression state and is abutted against the valve sleeve 1 and the valve core 2.

The valve sleeve 1 is provided with a first oil discharge port 11, a first oil control port 12, an oil inlet 13 and a second oil control port 14 at intervals along the axial direction in sequence on the circumferential side wall, the first oil discharge port 11 is located on one side of the valve sleeve 1 close to the opening, and a second oil discharge port 15 is arranged at one end of the valve sleeve 1 far away from the opening. The central axes of the first oil discharge port 11, the first oil control port 12, the oil inlet 13, the second oil control port 14 and the second oil discharge port 15 are located on the same plane, and a group is respectively arranged on two sides.

The second oil drain port 15 is arranged at the end of the valve sleeve 1, and compared with the structure that the original oil inlet 13, the first oil control port 12, the second oil control port 14, the first oil drain port 11 and the second oil drain port 15 are arranged on the circumferential side surface of the valve sleeve 1, the length of the valve sleeve 1 and the length of the valve core 2 can be shortened, the overall length of the control valve is further shortened, and the assembly difficulty of the control valve is reduced. The lengths of the valve sleeve 1 and the valve core 2 are shortened, and the machining processing precision of the valve core 2 and the valve sleeve 1 is easier to ensure. Correspondingly, the length of the hydraulic control module of the gearbox can be reduced, and the occupied space is reduced.

The valve core 2 is sequentially provided with a plurality of retaining rings at intervals along the axial direction, the retaining rings are integrally formed with the valve core 2, the diameter of each retaining ring is the same as the inner diameter of the valve sleeve 1, and the first retaining ring 21, the second retaining ring 22 and the third retaining ring 23 are sequentially arranged along the direction departing from the valve seat 4. The valve core 2 is pushed by the push rod 6 to compress the spring 3, the valve core 2 is provided with four adjusting positions, different oil circuit on-off in the control valve can be respectively realized, and the following four oil circuit states are provided:

when the valve core 2 is at the first adjusting position, the first oil discharge port 11 is communicated with the first oil control port 12, the first oil control port 12 is not communicated with the oil inlet 13, the oil inlet 13 is not communicated with the second oil control port 14, and the second oil control port 14 is communicated with the second oil discharge port 15;

when the valve core 2 is at the second adjusting position, the first oil discharge port 11 is not communicated with the first oil control port 12, the first oil control port 12 is communicated with the oil inlet 13, the oil inlet 13 is not communicated with the second oil control port 14, and the second oil control port 14 is communicated with the second oil discharge port 15;

when the valve core 2 is at the third adjusting position, the first oil discharge port 11 is communicated with the first oil control port 12, the first oil control port 12 is not communicated with the oil inlet 13, the oil inlet 13 is not communicated with the second oil control port 14, and the second oil control port 14 is communicated with the second oil discharge port 15;

when the valve core 2 is in the fourth adjusting position, the first oil discharge port 11 is communicated with the first oil control port 12, the first oil control port 12 is not communicated with the oil inlet 13, the oil inlet 13 is communicated with the second oil control port 14, and the second oil control port 14 is not communicated with the second oil discharge port 15.

An annular oil passing groove 211 is formed in the first baffle ring 21, an annular oil return groove 16 is formed in the valve sleeve 1 and between the first oil discharge port 11 and the first oil control port 12, and the width of the oil passing groove 211 is larger than the distance between the oil return groove 16 and the first oil control port; the width of the oil return groove 16 is larger than the distance between the oil passing groove 211 and the end surface of the first retainer ring 21 on the side close to the first oil outlet 11. The first baffle ring 21 moves axially to control the on-off of the first oil control port 12 and oil paths on two sides of the first baffle ring 21.

The distance between the first retainer ring 21 and the second retainer ring 22 is greater than the distance between the first oil control port 12 and the oil inlet 13, and the second retainer ring 22 axially moves to control the on-off of oil paths on two sides of the oil inlet 13 and the second retainer ring 22. The distance between the second retainer ring 22 and the third retainer ring 23 is greater than the distance between the oil inlet 13 and the second oil inlet 13, and the third retainer ring 23 moves axially to control the on-off of the oil paths on the two sides of the second oil control port 14 and the third retainer ring 23.

Referring to fig. 3 and 4, the width of the first retainer ring 21 is greater than the diameter of the first oil control port 12, and the distance between the inner side wall of the oil return groove 16 close to the first oil control port 12 and the oil inlet 13 is greater than the distance between the inner side wall of the oil passing groove 211 close to the first oil discharge port 11 and the side wall of the second retainer ring 22 close to the first retainer ring 21, so that an interference oil path generated by the communication between the oil inlet 13 and the first oil discharge port 11 can be prevented when the valve core 2 moves.

The width of the second retaining ring 22 is smaller than the diameter of the oil inlet 13, so that the axial contact length of each retaining ring and the valve sleeve 1 can be reduced, the lateral force borne by the valve core 2 is reduced, and the hysteresis of the electromagnetic valve is reduced.

The width of the third retainer ring 23 is larger than the diameter of the second oil control port 14, so that an interference oil path generated by communication between the oil inlet 13 and the second oil discharge port 15 can be prevented when the valve core 2 moves.

The implementation principle of the embodiment of the application is as follows:

referring to fig. 1 and 2, when the control valve is currentless, the spring 3 keeps the valve core 2 at the first adjusting position, the first oil discharge port 11 is communicated with the first oil control port 12, the first oil control port 12 is not communicated with the oil inlet 13, the oil inlet 13 is not communicated with the second oil control port 14, and the second oil control port 14 is communicated with the second oil discharge port 15. A part of hydraulic oil flows in from the first oil control port 12 and flows out from the first oil discharge port 11 through the oil passing groove 211 and the oil return groove 16, and a part of hydraulic oil flows in from the second oil control port 14 and then flows out from the second oil discharge port 15, corresponding to the state of the transmission when no gear shifting is required.

Referring to fig. 3 and 4, when the current increases, the push rod 6 pushes the valve core 2 to move towards the spring 3, the oil path between the oil inlet 13 and the first oil control port 12 gradually circulates, the oil path between the first oil control port 12 and the first oil discharge port 11 is gradually closed, the valve core 2 enters the second adjusting position, at this time, the first oil discharge port 11 is not communicated with the first oil control port 12, the first oil control port 12 is communicated with the oil inlet 13, the oil inlet 13 is not communicated with the second oil control port 14, and the second oil control port 14 is communicated with the second oil discharge port 15. The passage cross-sectional areas of the oil inlet 13 and the first oil control port 12 determine the flow of the hydraulic oil flowing out of the first oil control port 12.

Referring to fig. 5, when the current is further increased, the push rod 6 continues to push the valve core 2 to move towards the spring 3, the oil path between the oil inlet 13 and the first oil control port 12 is gradually cut off, the valve core 2 enters the third adjustment position, at this time, the first oil discharge port 11 is communicated with the first oil control port 12, the first oil control port 12 is not communicated with the oil inlet 13, the oil inlet 13 is not communicated with the second oil control port 14, the second oil control port 14 is communicated with the second oil discharge port 15,

referring to fig. 6, when the current continues to increase, the oil path between the second oil control port 14 and the second oil discharge port 15 is broken, the oil inlet 13 and the second oil control port 14 gradually circulate, the valve element 2 enters the fourth adjustment position, at this time, the first oil discharge port 11 is communicated with the first oil control port 12, the first oil control port 12 is not communicated with the oil inlet 13, the oil inlet 13 is communicated with the second oil control port 14, the second oil control port 14 is not communicated with the second oil discharge port 15, and the passage sectional area of the oil inlet 13 and the second oil control port 14 determines the flow rate of the hydraulic oil flowing out of the second oil control port 14.

The control function of the four-position flow of the control valve can be realized by using and switching the four states of the oil circuit in the control valve.

The embodiments of the present invention are preferred embodiments of the present application, and the protection scope of the present application is not limited thereby, wherein like parts are denoted by like reference numerals. Therefore, the method comprises the following steps: all equivalent changes made according to the structure, shape and principle of the present application shall be covered by the protection scope of the present application.

Claims (8)

1. A compact four-position four-way gear shifting control valve comprises a valve sleeve (1) with an opening at one end and a valve core (2) coaxially connected in the valve sleeve (1) in a sliding manner, and is characterized in that a first oil discharge port (11), a first oil control port (12), an oil inlet (13) and a second oil control port (14) are sequentially arranged on the circumferential side wall of the valve sleeve (1) at intervals along the axial direction, the first oil discharge port (11) is positioned on one side, close to the opening, of the valve sleeve (1), and a second oil discharge port (15) is arranged at one end, far away from the opening, of the valve sleeve (1); a plurality of baffle rings are fixedly connected to the valve core (2) at intervals in sequence along the axial direction, and the adjacent oil ports are controlled to be communicated or disconnected by the baffle rings.

2. The compact four-position four-way shift control valve according to claim 1, wherein a first retainer ring (21), a second retainer ring (22) and a third retainer ring (23) are sequentially arranged on the valve core (2), the diameters of the first retainer ring (21), the second retainer ring (22) and the third retainer ring (23) are equal to the inner diameter of the valve sleeve (1), and the first retainer ring (21) axially moves to control the on-off of the first oil control port (12) and oil paths on two sides of the first retainer ring (21); the second retaining ring (22) moves axially to control the on-off of the oil inlet (13) and oil ways on two sides of the second retaining ring (22); the third retainer ring (23) moves axially to control the on-off of the oil passages on the two sides of the second oil control port (14) and the third retainer ring (23).

3. The compact four-position four-way shift control valve according to claim 2, wherein an oil through groove (211) is formed in the first retainer ring (21), an oil return groove (16) is formed in the valve housing (1) and between the first oil discharge port (11) and the first oil control port (12), and the width of the oil through groove (211) is greater than the distance between the oil return groove (16) and the first oil control port (12); the width of the oil return groove (16) is larger than the distance between the oil passing groove (211) and the end surface of the first baffle ring (21) close to one side of the first oil outlet (11); the distance between the first retaining ring (21) and the second retaining ring (22) is larger than the distance between the first oil control port (12) and the oil inlet (13); the distance between the second retaining ring (22) and the third retaining ring (23) is larger than the distance between the oil inlet (13) and the second oil control port (14).

4. The compact four-position four-way shift control valve according to claim 3, wherein the width of the first retainer ring (21) is larger than the diameter of the first oil control port (12), and the distance between the inner side wall of the oil return groove (16) close to the first oil control port (12) and the oil inlet (13) is larger than the distance between the inner side wall of the oil through groove (211) close to the first oil discharge port (11) and the side wall of the second retainer ring (22) close to the first retainer ring (21).

5. A compact four-position four-way shift control valve according to claim 3, wherein the width of the second retainer ring (22) is smaller than the diameter of the oil inlet (13).

6. The compact four-position four-way shift control valve according to claim 3, wherein the width of the third retainer ring (23) is larger than the diameter of the second oil control port (14).

7. The compact four-position four-way gear shifting control valve is characterized in that a spring (3) is arranged in one end of the valve sleeve (1) provided with the second oil discharge port (15), one end of the spring (3) is abutted against the inner wall of the end face of the valve sleeve (1), and the other end of the spring is abutted against the end part of the valve core (2); valve barrel (1) opening one end is connected with disk seat (4), is provided with electromagnetic force driven plunger (5) in disk seat (4), and plunger (5) one end is connected with push rod (6), and disk seat (4) and case (2) butt are worn out to push rod (6) one end.

8. The compact four-position four-way shift control valve according to claim 1, wherein the first oil discharge port (11), the first oil control port (12), the oil inlet (13) and the second oil control port (14) radially penetrate through two sides of the valve sleeve (1).

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