A rotary "M" function electrically controlled reversing valve for a redundant pump-controlled hydraulic system

Abstract

A kind of rotating "M" function electric control reversing valve for redundancy pump-controlled hydraulic system, mainly comprising valve core, valve sleeve, limited angle motor and sealing ring.The valve sleeve is radially symmetrical to the central axis and has oil holes corresponding to the inlet and outlet ports of hydraulic pump and actuator respectively;The valve core is radially symmetrical to the central axis and has oil channel holes opposite to the valve sleeve, lateral cutting grooves communicating the inlet and outlet ports of hydraulic pump and oil tank, and pressure equalizing grooves reducing lateral force;The limited angle motor drives the valve core to rotate in the valve sleeve by spline under different driving voltage control, and the valve core is suspended at 0°-90°, the hydraulic pump and actuator are communicated at 0° position, and the hydraulic pump and actuator are isolated at 90° position;The sealing ring is used for directional sealing of oil.The present application is different from the slide valve type "M" reversing valve in structure, eliminates the problems of large throttling loss, unstable valve core state and large electromagnetic heating, and can be applied to the isolation of fault energy channel in redundancy pump-controlled hydraulic system.

Description

Technical Field

[0001] This application relates to the technical field of electrically controlled directional valves, and in particular to a rotary "M" functional electrically controlled directional valve for redundant pump-controlled hydraulic systems. Background Technology

[0002] The two-position four-way solenoid directional valve with "M" function is a key component of the fault energy channel in the isolation redundancy pump-controlled hydraulic servo system, and participates in system fault isolation and reconstruction.

[0003] Traditional "M" type two-position four-way solenoid directional valves are mostly used in valve-controlled hydraulic servo systems, with fixed high-pressure inlet and low-pressure outlet. Pump-controlled hydraulic servo systems, however, do not have fixed high and low pressure oil circuits; the pressure in both main oil circuits changes in real time with the load. Directly applying these valves to pump-controlled hydraulic servo systems results in functional and performance issues such as double-pass throttling losses at the inlet and outlet, unstable valve spool states, and excessive heat generation from the solenoid. Summary of the Invention

[0004] This application provides a rotary "M" functional electro-hydraulic directional valve for redundant pump-controlled hydraulic systems, which can isolate the faulty energy path of the redundant pump-controlled hydraulic servo system and solves the problems of large throttling loss, unstable valve core state and large electromagnet heating of traditional "M" type directional valves.

[0005] In a first aspect, an "M" functional electrically controlled directional valve is provided, wherein the "M" functional electrically controlled directional valve is applied to an oil manifold, the oil manifold including a first hydraulic pump channel, a second hydraulic pump channel, a first actuator channel, a second actuator channel, and a back pressure liquid tank port, and the "M" functional electrically controlled directional valve includes:

[0006] A valve sleeve is provided in the oil passage block. The valve sleeve has a first valve sleeve opening, a second valve sleeve opening, a third valve sleeve opening, and a fourth valve sleeve opening. The first valve sleeve opening is used to communicate with the first hydraulic pump passage, the second valve sleeve opening is used to communicate with the first actuator passage, the third valve sleeve opening is used to communicate with the second hydraulic pump passage, and the first valve sleeve opening is used to communicate with the second actuator passage.

[0007] A valve core is disposed within the valve sleeve. The valve core has a first valve core through hole, a second valve core through hole, and a side wall groove. The side wall groove is disposed on the side wall of the valve core and communicates with the back pressure liquid tank opening. The angular position of the valve core relative to the valve sleeve is either 0° or 90°.

[0008] When the valve core is at a 0° angle relative to the valve sleeve, the first valve core through hole is connected between the first valve sleeve opening and the second valve sleeve opening, and the second valve core through hole is connected between the third valve sleeve opening and the fourth valve sleeve opening.

[0009] When the valve core is at a 90° angle relative to the valve sleeve, the side wall groove is connected to the first valve sleeve opening, the third valve sleeve opening, the first hydraulic pump channel, and the second hydraulic pump channel.

[0010] Compared with the prior art, the solution provided in this application has at least the following beneficial technical effects:

[0011] When the valve core is at the 0° position, the axes of the two radial oil holes in the valve core and valve sleeve coincide, allowing flow in the two main oil passages on the pump source side and the load side, i.e., the connecting function. When the valve core is at the 90° position, the axes of the two radial oil holes in the valve core and valve sleeve are orthogonal and perpendicular, allowing flow in the two main oil passages on the pump source side through the valve core groove, while the oil ports of the two main oil passages on the load side are sealed by the valve core and valve sleeve surface seal, i.e., the "M" function. This achieves a rotary solution for a two-position four-way "M" function directional valve.

[0012] When the valve core is in the 0° position (interchange function), the oil holes in the valve core and valve sleeve are designed to be the same size and aligned. At this time, the oil flows without throttling. When the valve core is in the 90° position (M function), both main oil circuits on the pump source side are directly connected to the groove on the upper part of the valve core. The above design eliminates the pressure loss at the throttling window of the traditional "M" function valve core, realizing oil flow without throttling loss.

[0013] At the same time, when the valve core is in the 90° position, i.e. the "M" function, the two oil ports on the oil pump side communicate with the oil tank through the cutting groove. This avoids the problem of poor oil suction and local vacuum caused by the hydraulic pump still rotating after the fault energy channel is isolated. It also eliminates the hidden danger of oil gas precipitation and subsequent cavitation of local components.

[0014] When the valve core is in the 0° position (interchange function), the oil holes in the valve core and valve sleeve are the same size and aligned, eliminating the influence of hydraulic forces. When the valve core is in the 90° position ("M" function), the grooves on the valve core are aligned with the two oil ports on the pump side. At this time, the valve core is structurally symmetrical relative to both the pump side and the load side, and the circumferential force of the oil on the valve core is canceled out. Therefore, the valve core can maintain a stable position under the frictional torque of the sealing ring, eliminating the instability in the working state caused by the hydraulic forces that affect the valve core in traditional "M" type directional valves.

[0015] In conjunction with the first aspect, in some implementations of the first aspect, the sidewall groove is a symmetrical structure with respect to the cross section perpendicular to the extension direction of the first valve core through hole.

[0016] When the valve core is at a 90° position relative to the valve sleeve, the side wall groove can be a symmetrical structure relative to the section perpendicular to the extension direction of the first valve core through hole and passing through the valve core central axis, so as to reduce the force of hydraulic pressure on the side wall of the side wall groove and avoid the valve core from rotating under hydraulic pressure.

[0017] In conjunction with the first aspect, in some implementations of the first aspect, the bottom wall of the valve core is provided with a bottom wall groove, which connects the side wall groove and the back pressure liquid tank opening.

[0018] By increasing the back pressure of the oil through the bottom wall groove, the valve core is kept in a suspended state, which greatly reduces the friction when the valve core rotates, reduces the motor load, and thus improves the response capability.

[0019] In conjunction with the first aspect, in some implementations of the first aspect, the bottom wall groove is a symmetrical structure relative to the cross section perpendicular to the extension direction of the first valve core through hole and passing through the valve core central axis.

[0020] When the valve core is at a 90° position relative to the valve sleeve, the bottom wall groove can be a symmetrical structure relative to the section perpendicular to the extension direction of the first valve core through hole and passing through the valve core central axis, so as to reduce the force of hydraulic pressure on the side wall of the bottom wall groove and avoid the valve core from rotating under hydraulic pressure.

[0021] In conjunction with the first aspect, in some implementations of the first aspect, the "M" functional electrically controlled directional valve further includes:

[0022] An electric motor is used to rotate the valve core. The electric motor includes a motor shaft and a bearing. The motor shaft is connected to the valve core, and the bearing is engaged with the motor shaft. The bearing is a tapered roller bearing or an angular contact ball bearing.

[0023] The motor shaft is fixed with a tapered roller bearing, and the valve core is connected to the motor shaft by a spline. The bottom of the valve core is connected to the oil tank. The back pressure of the oil causes the bottom of the valve core to detach from the bottom surface of the mounting hole, thus avoiding friction at the end of the valve core.

[0024] In conjunction with the first aspect, in some implementations of the first aspect, the "M" functional electrically controlled directional valve further includes:

[0025] A first sealing ring is disposed on the outer periphery of the valve sleeve and located on the side of the first valve sleeve opening and the second valve sleeve opening away from the third valve sleeve opening.

[0026] The first sealing ring can isolate the first hydraulic pump channel from the outside world.

[0027] In conjunction with the first aspect, in certain implementations of the first aspect, the "M" functional electrically controlled directional valve further includes:

[0028] The second sealing ring is disposed on the outer periphery of the valve sleeve and located between the first valve sleeve opening and the third valve sleeve opening.

[0029] The second sealing ring 4 can isolate the first hydraulic pump channel P1 from the second hydraulic pump channel P2.

[0030] In conjunction with the first aspect, in some implementations of the first aspect, the "M" functional electrically controlled directional valve further includes:

[0031] The third sealing ring is disposed on the outer periphery of the valve sleeve and is located on the side of the third valve sleeve opening and the fourth valve sleeve opening away from the first valve sleeve opening.

[0032] The third sealing ring 5 can isolate the second hydraulic pump channel P2 from the back pressure liquid tank port T.

[0033] In conjunction with the first aspect, in some implementations of the first aspect, the "M" functional electrically controlled directional valve further includes:

[0034] A fourth sealing ring is disposed on the outer periphery of the valve core and located on the side of the first valve core through hole away from the side wall groove.

[0035] When the valve core is in the 0° and 90° positions (communication and isolation states), its stability is maintained solely by the frictional torque of the sealing ring. In this state, the motor can be controlled with low voltage to further maintain position stability. If there is a pump source failure, requiring the valve core to switch from the 0° to the 90° position (communication to "M"), the motor switches to rated voltage control to output a larger torque to overcome the frictional force of the sealing ring and the hydraulic force at the oil port to complete the switching process. Throughout the entire operation, the motor is essentially in a reduced-voltage control state, resulting in minimal motor heat generation.

[0036] In conjunction with the first aspect, in some implementations of the first aspect, a pressure equalization groove is provided around the outer periphery of the valve core, and the pressure equalization groove is connected to the side wall recess.

[0037] The equalizing tank and the cutting tank are connected together and connected to the low-pressure oil in the oil tank, thereby eliminating the lateral force generated by the high-pressure oil on the valve core and the circumferential friction force generated by the high-pressure oil squeezing and deforming the sealing ring.

[0038] In conjunction with the first aspect, in some implementations of the first aspect, the first valve sleeve opening and the second valve sleeve opening are arranged opposite to each other, the third valve sleeve opening and the fourth valve sleeve opening are arranged opposite to each other, and the extension directions of the first valve core through hole and the second valve core through hole are both arranged perpendicular to the central axis of the valve core.

[0039] When the valve core is in the 0° position, i.e., in the communication function, the two main oil circuits on the pump source side and the load side are respectively circulated, and the oil holes on the valve core and the valve sleeve are of equal size and directly opposite each other; when the valve core is in the 90° position, i.e. in the "M" function, the two main oil circuits on the pump source side are directly connected to the recessed groove on the valve core; the above designs have eliminated the pressure loss at the throttling window of the valve core in the traditional "M" function valve.

[0040] In a second aspect, a redundant pump-controlled hydraulic system is provided, the redundant pump-controlled hydraulic system including the “M” functional electro-hydraulic directional valve as described in any of the implementations of the first aspect above. Attached Figure Description

[0041] Figure 1 This is a schematic structural diagram of a rotary "M" functional electrically controlled directional valve provided in an embodiment of this application.

[0042] Figure 2 This is a schematic structural diagram of a rotary "M" functional electrically controlled directional valve provided in an embodiment of this application.

[0043] Figure 3 This is a schematic diagram illustrating the application of a rotary "M" functional electrically controlled directional valve in a redundant pump-controlled hydraulic servo system, as provided in this application embodiment.

[0044] Figure 4 for Figure 3 The diagram shows a schematic of the symbol for a rotary "M" functional electrically controlled directional valve.

[0045] Figure 5 This is a control principle diagram of a rotary "M" functional electrically controlled directional valve provided in an embodiment of this application. Detailed Implementation

[0046] The present application will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0047] Figure 1 and Figure 2 This is a schematic structural diagram of a rotary "M" functional electrically controlled directional valve provided in an embodiment of this application. Figure 1 and Figure 2 The “M” functional electro-hydraulic directional valve shown can be used in redundant pump-controlled hydraulic systems.

[0048] The "M" functional electrically controlled directional valve may include a valve core 1 and a valve sleeve 2. The valve sleeve 2 may have a hollow tubular structure. The valve sleeve 2 has a first valve sleeve opening 21, a second valve sleeve opening 22, a third valve sleeve opening 23, and a fourth valve sleeve opening 24. The orifice axis of each valve sleeve opening may be perpendicular to the central axis of the valve sleeve 2. The first valve sleeve opening 21 and the second valve sleeve opening 22 may be symmetrically arranged with respect to the central axis of the valve sleeve 2, and the third valve sleeve opening 23 and the fourth valve sleeve opening 24 may also be symmetrically arranged with respect to the central axis of the valve sleeve 2.

[0049] The valve sleeve 2 can be mechanically fixed in the mounting hole of the hydraulic manifold 8. The sidewall of the hydraulic manifold 8 can be provided with a first hydraulic pump channel P1 and a second hydraulic pump channel P2. In one possible scenario, the hydraulic pressure in the first hydraulic pump channel P1 can be higher than that in the second hydraulic pump channel P2; in another possible scenario, the hydraulic pressure in the first hydraulic pump channel P1 can be lower than that in the second hydraulic pump channel P2. That is, the first hydraulic pump channel P1 and the second hydraulic pump channel P2 can alternately serve as the load output pressure and back pressure. The sidewall of the hydraulic manifold 8 can also be provided with a first actuator channel A and a second actuator channel B. In some embodiments, the first actuator channel A can be disposed opposite to the first hydraulic pump channel P1, and the second actuator channel B can be disposed opposite to the second hydraulic pump channel P2.

[0050] like Figure 1 and Figure 2 As shown, when the "M" functional electrically controlled directional valve is installed in the hydraulic manifold 8, the first hydraulic pump channel P1 of the hydraulic manifold 8 can communicate with the first valve sleeve opening 21 of the valve sleeve 2, the first actuator channel A of the hydraulic manifold 8 can communicate with the second valve sleeve opening 22 of the valve sleeve 2, the second hydraulic pump channel P2 of the hydraulic manifold 8 can communicate with the third valve sleeve opening 23 of the valve sleeve 2, and the second actuator channel B of the hydraulic manifold 8 can communicate with the fourth valve sleeve opening 24 of the valve sleeve 2. The bottom of the valve sleeve 2 can communicate with the back pressure liquid tank port T of the hydraulic manifold 8.

[0051] A valve core 1 can be installed in the central inner hole of the valve sleeve 2. The valve core 1 and the valve sleeve 2 can be ground together. The valve core 1 has a first valve core through hole 11 and a second valve core through hole 12. The axes of the first valve core through hole 11 and the second valve core through hole 12 are both perpendicularly intersecting the central axis of the valve sleeve 2. That is to say, the first valve core through hole 11 and the second valve core through hole 12 can be symmetrically arranged with respect to the central axis of the valve sleeve 2.

[0052] The sidewall of the valve core 1 may be provided with a sidewall groove 13. One end of the sidewall groove 13 may be positioned opposite to the first valve core through hole 11 and extend along the central axis of the valve sleeve 2 toward the second valve core through hole 12 to the bottom of the valve core 1. The extending direction of the sidewall groove 13 may be perpendicular to the hole axis direction of the first valve core through hole 11 or the second valve core through hole 12.

[0053] The bottom wall of the valve core 1 may be provided with a bottom wall groove 14. The bottom wall groove 14 may communicate with the side wall groove 13. The extending direction of the bottom wall groove 14 may intersect perpendicularly with respect to the central axis of the valve sleeve 2. Figure 1 and Figure 2 As shown, when the "M" functional electronic control reversing valve is installed in the oil circuit block 8, the bottom wall trough 14 can be connected to the back pressure liquid tank port T of the oil circuit block 8.

[0054] When valve core 1 is at 0° relative to valve sleeve 2, such as Figure 1 As shown, the first valve core through hole 11 can be connected between the first valve sleeve opening 21 and the second valve sleeve opening 22, and the second valve core through hole 12 can be connected between the third valve sleeve opening 23 and the fourth valve sleeve opening 24, thereby forming a communication function. When the valve core 1 rotates relative to the valve sleeve 2 at a 90° position, the side wall groove 13 of the valve core 1 can move closer to the first hydraulic pump channel P1 and the second hydraulic pump channel P2 of the valve sleeve 2.

[0055] When valve core 1 is at a 90° position relative to valve sleeve 2, such as Figure 2 As shown, the extension directions of the first valve core through hole 11 and the second valve core through hole 12 have been rotated. The first valve core through hole 11 no longer communicates with the first valve sleeve opening 21 and the second valve sleeve opening 22, and the second valve core through hole 12 no longer communicates with the third valve sleeve opening 23 and the fourth valve sleeve opening 24. Due to the grinding fit between the valve core 1 and the valve sleeve 2, the first valve core through hole 11 and the second valve core through hole 12 can be blocked by the sealing surface of the valve sleeve 2. The first actuator channel A and the second actuator channel B on the actuator side are blocked by the sealing surface. The first hydraulic pump channel P1 and the second hydraulic pump channel P2 of the valve sleeve 2 can communicate with the side wall groove 13 of the valve core 1, and are connected to the back pressure liquid tank port T of the oil circuit block 8 through the bottom wall groove 14, thereby forming the "M" function.

[0056] When the valve core 1 is at a 90° position relative to the valve sleeve 2, the side wall groove 13 and the bottom wall groove 14 can be symmetrical structures relative to the cross section that is perpendicular to the extension direction of the first valve core through hole 11 and passes through the valve core central axis. This reduces the force of the oil on the side walls of the side wall groove 13 and the bottom wall groove 14, and prevents the valve core 1 from rotating under hydraulic pressure.

[0057] In some embodiments, the "M" functional electrically controlled directional valve may further include a motor 7. The motor 7 may be a limited-angle motor. The motor 7 can be used to rotate the valve core 1, causing the angular position of the valve core 1 relative to the valve sleeve 2 to switch between 0° and 90°. That is, the motor 7 can drive the valve core 1 to rotate within the valve core's inner bore in the range of 0° to 90°.

[0058] The motor shaft 72 of the motor 7 can be connected to the valve core 1. Through the back pressure liquid tank port T of the oil circuit block 8, under the action of the back pressure of the oil tank, the bottom end of the valve core 1 can be set with a gap to the back pressure liquid tank port T of the oil circuit block 8, so that the valve core 1 is in a suspended state, which greatly reduces the friction when the valve core 1 rotates. Therefore, the rotation of the valve core 1 will not rub against the bottom wall of the oil circuit block 8.

[0059] The top end of the valve core 1 can be pressed against the motor shaft 72. The motor 7 may also include a bearing 71. The bearing 71 can provide support for the motor shaft 72. In some embodiments, the bearing 71 can be a tapered roller bearing or an angular contact ball bearing. Both tapered roller bearings and angular contact ball bearings can have the ability to withstand axial clamping forces, so that the bearing 71 can withstand the clamping force from the valve core 1.

[0060] In some embodiments, a first sealing groove may be provided on the outer periphery of the valve sleeve 2. The first sealing groove may be located on the side of the first valve sleeve opening 21 and the second valve sleeve opening 22 that is away from the third valve sleeve opening 23 or the fourth valve sleeve opening 24. When the valve sleeve 2 is disposed within the oil passage block 8, the first sealing groove may be used to accommodate the first sealing ring 3, which may isolate the first hydraulic pump passage P1 from the outside environment.

[0061] In some embodiments, a second sealing groove may be provided on the outer periphery of the valve sleeve 2. The second sealing groove may be located between the first valve sleeve opening 21 and the third valve sleeve opening 23, and between the second valve sleeve opening 22 and the fourth valve sleeve opening 24. When the valve sleeve 2 is disposed within the oil passage block 8, the second sealing groove may be used to accommodate the second sealing ring 4, which may isolate the first hydraulic pump passage P1 from the second hydraulic pump passage P2.

[0062] In some embodiments, a third sealing groove may be provided on the outer periphery of the valve sleeve 2. The third sealing groove may be located on the side of the third valve sleeve opening 23 and the fourth valve sleeve opening 24 that is away from the first valve sleeve opening 21 or the second valve sleeve opening 22. When the valve sleeve 2 is disposed within the oil passage block 8, the third sealing groove may be used to accommodate the third sealing ring 5, which may isolate the second hydraulic pump passage P2 from the back pressure liquid tank opening T.

[0063] In some embodiments, a fourth sealing groove may be provided on the outer periphery of the valve core 1. The fourth sealing groove may be located on the side of the first valve core through hole 11 away from the second valve core through hole 12. The fourth sealing ring 6 is fitted inside the fourth sealing groove to isolate the working fluid from the outside environment.

[0064] In some embodiments, one or more pressure-equalizing grooves may be provided on the outer periphery of the valve core 1 to eliminate the radial lateral force of the valve core 1, thereby reducing the radial offset of the valve core 1. For example... Figure 1 and Figure 2 As shown, the outer periphery of the valve core 1 may be provided with a first pressure equalizing groove 15, a second pressure equalizing groove 16, and a third pressure equalizing groove 17. The first pressure equalizing groove 15 may be located between the first valve core through hole 11 and the fourth sealing groove. The second pressure equalizing groove 16 may be located between the first valve core through hole 11 and the second valve core through hole 12. The third pressure equalizing groove 17 may be located on the side of the second valve core through hole 12 away from the first valve core through hole 11.

[0065] Figure 3 This is a schematic diagram illustrating the application of a rotary "M" functional electrically controlled directional valve in a redundant pump-controlled hydraulic servo system, as provided in an embodiment of this application. Figure 4 This is a schematic diagram of the symbol for a rotary "M" functional electrically controlled directional valve. Figure 5 This is a control principle diagram of a rotary "M" functional electrically controlled directional valve provided in an embodiment of this application. When all energy channels of the redundant pump-controlled hydraulic servo system are normal, the directional valve is in a communication state, and the finite angle motor operates at the 0° position, powered by -15VDC. If energy channel B fails, when the directional valve is activated for isolation, it is powered by +28VDC, outputting a larger torque to ensure directional switching is completed. After directional switching is completed, the finite angle motor operates at the 90° position, powered by +15VDC. The directional valve operates primarily at a reduced voltage of 15VDC throughout its entire range, reducing motor heat generation.

[0066] In some embodiments, when the finite angle motor needs to rotate from a 90° position back to a 0° position, it can be powered by -28VDC to output a larger torque to ensure the commutation is completed; after the commutation is completed, the finite angle motor operates at the 0° position and is powered by -15VDC. Alternatively, it can be achieved through mechanical rotation.

[0067] Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make possible changes and modifications without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope defined in the claims of the present invention.

Claims

1. An "M" functional electrically controlled directional valve, wherein the "M" functional electrically controlled directional valve is applied to an oil circuit block (8), the oil circuit block (8) comprising a first hydraulic pump channel (P1), a second hydraulic pump channel (P2), a first actuator channel (A), a second actuator channel (B), and a back pressure liquid tank port (T), characterized in that, The "M" functional electrically controlled reversing valve includes: A valve sleeve (2) is used to be fixed inside the oil passage block (8). The valve sleeve (2) has a first valve sleeve opening (21), a second valve sleeve opening (22), a third valve sleeve opening (23), and a fourth valve sleeve opening (24). The first valve sleeve opening (21) is used to communicate with the first hydraulic pump channel (P1), the second valve sleeve opening (22) is used to communicate with the first actuator channel (A), the third valve sleeve opening (23) is used to communicate with the second hydraulic pump channel (P2), and the first valve sleeve opening (24) is used to communicate with the second actuator channel (B). A valve core (1) is disposed inside the valve sleeve (2). The valve core (1) has a first valve core through hole (11), a second valve core through hole (12), and a side wall groove (13). The side wall groove (13) is disposed on the side wall of the valve core (1). The side wall groove (13) is connected to the back pressure liquid tank opening (T). The angular position of the valve core (1) relative to the valve sleeve (2) is 0° or 90°. When the valve core (1) is at an angle of 0° relative to the valve sleeve (2), the first valve core through hole (11) is connected between the first valve sleeve opening (21) and the second valve sleeve opening (22), and the second valve core through hole (12) is connected between the third valve sleeve opening (23) and the fourth valve sleeve opening (24). When the valve core (1) is at a 90° angle relative to the valve sleeve (2), the side wall groove (13) is connected to the first valve sleeve opening (21), the third valve sleeve opening (23), the first hydraulic pump channel (P1), and the second hydraulic pump channel (P2).

2. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The sidewall groove (13) is a symmetrical structure relative to the section that is perpendicular to the extension direction of the first valve core through hole (11) and passes through the central axis of the valve core (1).

3. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The bottom wall of the valve core (1) is provided with a bottom wall groove (14), which is connected between the side wall groove (13) and the back pressure liquid tank opening (T).

4. The "M" functional electrically controlled directional valve according to claim 3, characterized in that, The bottom wall groove (14) is a symmetrical structure relative to the section that is perpendicular to the extension direction of the first valve core through hole (11) and passes through the central axis of the valve core (1).

5. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The "M" functional electrically controlled reversing valve also includes: The motor (7) is used to rotate the valve core (1). The motor (7) includes a motor shaft (71) and a bearing (72). The motor shaft (71) is splined to the valve core (1). The bearing (72) is engaged with the motor shaft (71). The bearing (72) is a tapered roller bearing (72) or an angular contact ball bearing (72).

6. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The "M" functional electrically controlled reversing valve also includes: The first sealing ring (3) is disposed on the outer periphery of the valve sleeve (2) and is located on the side of the first valve sleeve opening (21) and the second valve sleeve opening (22) away from the third valve sleeve opening (23).

7. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The "M" functional electrically controlled reversing valve also includes: The second sealing ring (4) is disposed on the outer periphery of the valve sleeve (2) and located between the first valve sleeve opening (21) and the third valve sleeve opening (23).

8. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The "M" functional electrically controlled reversing valve also includes: The third sealing ring (5) is disposed on the outer periphery of the valve sleeve (2) and is located on the side of the third valve sleeve opening (23) and the fourth valve sleeve opening (24) away from the first valve sleeve opening (21).

9. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The "M" functional electrically controlled reversing valve also includes: The fourth sealing ring (6) is disposed on the outer periphery of the valve core (1) and located on the side of the first valve core through hole (11) away from the side wall groove (13).

10. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The valve core (1) is surrounded by pressure equalization grooves (15), (16), and (17), and the pressure equalization grooves are connected to the side wall sink groove (13).

11. The "M" functional electrically controlled directional valve according to claim 1, characterized in that, The first valve sleeve opening (21) and the second valve sleeve opening (22) are arranged opposite to each other, the third valve sleeve opening (23) and the fourth valve sleeve opening (24) are arranged opposite to each other, and the extension directions of the first valve core through hole (11) and the second valve core through hole (12) are both arranged perpendicular to the central axis of the valve core (1).

12. The "M" functional electrically controlled directional valve according to claim 5, characterized in that, The tapered roller bearing (72) or angular contact ball bearing (72) is also fitted on the shaft shoulder of the valve core (1) and installed in the shoulder hole of the valve sleeve (2).

13. A redundant pump-controlled hydraulic system, characterized in that, The redundant pump-controlled hydraulic system includes an "M" functional electrically controlled directional valve as described in any one of claims 1 to 12.

Images