CN203176030U - Multi-control variable damping double-freedom-degree valve core rotary four-way reversing valve - Google Patents

Abstract

The utility model discloses a multi-control variable damping double-freedom-degree valve core rotary four-way reversing valve. A valve core is composed of a first valve core body and a second valve core body. A first boss is arranged on the first valve core body, a second boss, a third boss, a fourth boss, a fifth boss and a sixth boss are arranged on the second valve core body, the first boss, the second boss, the third boss, the fourth boss, the fifth boss and the sixth boss are arranged in the direction from a first end cover to a second end cover in sequence, a corresponding cavity is formed between each two adjacent bosses, a valve body wall where the corresponding cavities are located and a valve body wall where the bosses are located are provided with corresponding oil ports and/or flow channels, grooves formed at the end face of the third boss and the end face of the fourth boss, a spring is arranged inside the cavity formed between the first boss and the second boss, four axial flow channels are arranged on the sixth boss, and the axial flow channels respectively form cavity flow with the fifth boss and the sixth boss. The multi-control variable damping double-freedom-degree valve core rotary four-way reversing valve has two freedom degrees of valve core rotation and valve core axial motion, independent control is conducted on work frequency and amplitude displacement of an executing mechanism through multiple control methods.

Description

Multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve

technical field

The utility model relates to a hydraulic reversing valve, which is mainly used in the technical field of engineering where the working frequency and the displacement amplitude of the actuator can be independently controlled.

Background technique

A rotary valve refers to a valve that realizes the on-off and reversing of the oil circuit through the rotation of the spool. The existing rotary valve basically has only one degree of freedom of rotation of the spool, which causes the coupling of the rotary valve to the control of the operating frequency and displacement amplitude of the actuator, that is, the work of the actuator can only be controlled at the same time through the rotation degree of freedom of the spool. Frequency and amplitude displacement, however, many engineering technical fields require independent control of the operating frequency and amplitude displacement of the actuator. the

Utility model content

The purpose of this utility model is to overcome the deficiencies of the prior art, and provide a multi-control variable damper that can be applied to high-pressure and large-flow occasions, independently control the operating frequency and amplitude displacement of the actuator, and can adjust the damping of the hydraulic system. Two-degree-of-freedom spool rotary four-way reversing valve.

In order to achieve the above purpose, the technical solution adopted by the utility model is: the utility model multi-control variable damping dual-degree-of-freedom valve core rotary four-way reversing valve, including a valve body, a valve sleeve, a valve core, a first end cover and the second end cap, the feature is: the valve core is composed of the first valve core and the second valve core; the first valve core is provided with a first boss, and the second valve core is provided with a second protrusion Platform, third boss, fourth boss, fifth boss and sixth boss, first boss, second boss, third boss, fourth boss, fifth boss, sixth boss The platforms are arranged in sequence along the direction from the first end cover to the second end cover;

The first end of the first spool runs through and protrudes from the first end cover, and the first end of the first spool is either connected to the main shaft of the stepper motor through a coupling, or connected to the rotor of the rotary proportional electromagnet; The second end of the first spool is opposite to the first end of the second spool and forms a first cavity between the first boss and the second boss. One chamber communicates with the fuel tank; a spring is arranged in the first chamber, and the second end of the first spool and the first end of the second spool extend into the spring, and one end of the spring is connected to the first end of the second spool. The second spool is fixedly connected, and the other end of the spring is fixedly connected to the first spool;

The second end cover is provided with a radial fourth oil port, a first axial flow channel and an axial through hole, the fourth oil port communicates with the first axial flow channel, and the fourth oil port communicates with the first axial flow channel. The axial through hole communicates with each other, and the second end of the second valve core extends into the axial through hole and closely cooperates with each other;

The outer end surface of the sixth boss is in close contact with the second end cover, and the sixth boss is provided with a second axial flow channel, a third axial flow channel, a fourth axial flow channel and a fifth axial flow channel , the fifth cavity is formed between the fifth boss and the sixth boss, and the second axial flow channel, the third axial flow channel, the fourth axial flow channel, and the fifth axial flow channel are respectively connected with the fifth cavity In communication, the valve body wall where the fifth chamber is located has a third oil port that communicates the fifth chamber with the oil supply system and a sixth axial flow passage that enables the fifth chamber to communicate with the first axial flow passage;

A second chamber is formed between the second boss and the third boss, and the valve body wall where the second chamber is located is provided with a first oil return port that enables the second chamber to communicate with the oil tank and enables the second chamber to communicate with the second chamber. A seventh axial flow passage communicated with one cavity, and variable damping is installed on the internal thread of the seventh axial flow passage; a third cavity is formed between the third boss and the fourth boss, and the valve where the third cavity is located There is a P oil inlet on the body wall that can communicate the third chamber with the oil supply system; a fourth chamber is formed between the fourth boss and the fifth boss, and the wall of the valve body where the fourth chamber is located is opened to allow The second oil return port where the fourth cavity communicates with the oil tank;

A oil port for controlling the actuator is opened on the valve body wall where the third boss is located, and a B oil port for controlling the actuator is opened on the valve body wall where the fourth boss is located;

On one end surface of the third boss, there are first grooves that can communicate with the first oil return port and A oil port at intervals along the circumferential direction, and on the other end surface of the third boss at intervals along the circumferential direction. There is a second groove that can connect the P oil inlet with the A oil port; on one end surface of the fourth boss, there are spaced apart along the circumferential direction the first groove that can connect the P oil inlet with the B oil port. Three grooves, on the other end surface of the fourth boss, there are fourth grooves that can communicate with the second oil return port and B oil port at intervals along the circumferential direction; the first groove and the corresponding second groove The projections of the grooves on the projection plane perpendicular to the central axis of the second valve core overlap each other, and the projections of the third groove and the corresponding fourth groove on the projection plane perpendicular to the central axis of the second valve core overlap each other, The projections of the second groove and the third groove on the projection plane perpendicular to the central axis of the second valve core are arranged alternately and staggered along the circumferential direction;

The valve sleeve has corresponding first valve sleeve windows, second valve sleeve windows, and third valve sleeve windows at the positions where the first groove, the second groove, the third groove and the fourth groove are located. and the fourth valve sleeve window, the projections of the first valve sleeve window and the corresponding fourth valve sleeve window on the projection plane perpendicular to the central axis of the second valve core overlap each other, and the second valve sleeve window and the corresponding first valve sleeve window The projections of the three valve sleeve windows on the projection plane perpendicular to the central axis of the second valve core overlap each other, and the first valve sleeve window and the second valve sleeve window are on the projection plane perpendicular to the central axis of the second valve core. The projections of are alternately staggered along the circumferential direction.

Further, the first groove and the second groove of the utility model are evenly distributed along the circumferential direction of the end surface of the third boss, and the third groove and the fourth groove are distributed along the end surface of the fourth boss. Evenly distributed in the circumferential direction of the end face.

Further, the first valve sleeve window, the second valve sleeve window, the third valve sleeve window and the fourth valve sleeve window of the utility model are respectively uniformly distributed along the circumferential direction of the valve sleeve.

Compared with the prior art, the utility model has the advantages of large power, large flow, good high-frequency performance, strong load adaptability, and good anti-pollution performance; it has two degrees of freedom of valve core rotation and valve core axial movement , can independently control the operating frequency and amplitude displacement of the actuator, that is, the stepper motor drives the valve core to rotate, and then controls the operating frequency of the actuator, and the combined effect of the active hydraulic pressure and the spring pre-adjustment force controls the axial direction of the valve core. Move, and then control the amplitude displacement of the actuator. The axial displacement of the control spool has a variety of control methods, and the adaptability to working conditions is strong. The damping ratio of the system can be adjusted through variable damping, and the working performance of the system can be adjusted.

Description of drawings

Figure 1 is a schematic diagram of the internal structure of the multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve of the utility model, wherein the valve body, valve sleeve and end cap are central longitudinal sectional views;

Fig. 2 is a three-dimensional structural schematic diagram of the valve body of the utility model multi-control variable damping dual-degree-of-freedom valve core rotary four-way reversing valve cut along the central longitudinal section of the valve body;

Fig. 3 is a three-dimensional structural schematic diagram of the valve sleeve 2;

Fig. 4 is a three-dimensional structural schematic view of the first valve core 3;

Fig. 5 is a three-dimensional structural schematic view of the second valve core 4;

Fig. 6 is an enlarged view of part A in Fig. 1 when the multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve of the utility model is in the P→B working state (that is, the first working state);

Fig. 7 is an enlarged view of part A in Fig. 1 when the reversing valve of the present invention is in the P→A working state (that is, the second working state);

Fig. 8 is a schematic diagram of the projected position distribution relationship between the second groove and the third groove on the projected plane perpendicular to the central axis of the second valve core;

Fig. 9 is a schematic diagram of the internal structure of the reversing valve of the present invention after the second end cap is rotated by 180°, wherein the valve body, valve sleeve and end cap are central longitudinal cross-sectional views.

In the figure, 1—valve body; 2—valve sleeve; 3—first spool; 4—second spool; 5—first end cap; 6—second end cap; 7—first boss; 8— The second boss; 9—the third boss; 10—the fourth boss; 11—the fifth boss; 12—the sixth boss; 13—the first end of the first spool; 14—the first spool 15—the first end of the second spool; 16—the second end of the second spool; 17—the spring; 18—one end of the spring; 19—the other end of the spring; 20—the first cavity; 21—second cavity; 22—third cavity; 23—fourth cavity; 24—fifth cavity; 25—axial through hole; 26—first axial flow channel; 27—second axial flow channel; 28 - the third axial channel; 29 - the fourth axial channel; 30 - the fifth axial channel; 31 - the sixth axial channel; 32 - the seventh axial channel; 33 - variable damping; 34—fourth oil port; 35—third oil port; 36—oil return port; 37—P oil inlet; 38—oil return port; 39—A oil port; 40—B oil port; 41—first groove Groove; 42—the second groove; 43—the third groove; 44—the fourth groove; 45—the first valve sleeve window; 46—the second valve sleeve window; 47—the third valve sleeve window; 48—the first Four valve sleeve windows; 49—oil drain port.

Detailed ways

Below in conjunction with accompanying drawing and embodiment the utility model is further described.

As shown in Figures 1 to 5, the multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve of the utility model mainly includes a valve body 1, a valve sleeve 2, a first spool 3, and a second spool 4. The first end cap 5 and the second end cap 6 . The first valve core 3 and the second valve core 4 are placed in the cavity of the valve body 1 , and the first end cover 5 and the second end cover 6 are installed together with the valve body 1 at the end faces of the two ends of the valve body 1 respectively. As shown in Figure 1, Figure 4 and Figure 5, a first boss 7 is provided on the first valve core 3, and a second boss 8, a third boss 9, a fourth boss 4 are provided on the second valve core 4. The boss 10, the fifth boss 11 and the sixth boss 12, and the first boss 7, the second boss 8, the third boss 9, the fourth boss 10, the fifth boss 11 and the sixth boss The stages 12 are sequentially arranged along the direction from the first end cover 5 to the second end cover 6 . The first end 13 of the first spool runs through and extends out of the first end cover 5. The first end 13 of the first spool can be connected to the main shaft of the stepping motor through a coupling, and the main shaft of the stepping motor drives the spool to realize The rotary motion of the spool constitutes an open-loop control system with simple structure, convenient operation, good high-frequency performance and good anti-pollution performance. As another embodiment of the present invention, the first end 13 of the first spool can also be connected with the rotor of the rotating proportional electromagnet through a coupling, and the rotor of the rotating proportional electromagnet drives the spool and realizes the rotation of the spool. Rotational movement, and adding an angle sensor to realize the feedback control of the angular displacement of the spool, constitutes a closed-loop control system, which has strong load adaptability and improves control accuracy and stability.

As shown in Figure 1, the first chamber 20 is a cavity formed between the first boss 7 and the second boss 8, and the wall of the valve body 1 where the first chamber 20 is located has a hole that enables the first chamber 20 to be connected to the second boss 8. The oil drain port 49 communicated with the oil tank, the leakage oil entering the first cavity 20 can flow back to the oil tank through the oil drain port 49 . The spring 17 is located in the first chamber 20, the second end 14 of the first spool and the first end 15 of the second spool extend into the spring 17, and the second end 14 of the first spool and the second end of the second spool The first end 15 is opposite, one end 18 of the spring is fixedly connected to the second valve core 4 , and the other end 18 of the spring is fixedly connected to the first valve core 3 . The second end cover 6 is provided with a fourth radial oil port 34 , a first axial channel 26 and an axial through hole 25 . The fourth oil port 34 communicates with the first axial channel 26 , and the fourth oil port 34 communicates with the axial through hole 25 . The second end 16 of the second spool extends into the axial through hole 25 to form a tight fit with the axial through hole 25 . Compared with other bosses, the sixth boss 12 is closest to the second end cap 6 . The outer end surface of the sixth boss 12 is in close contact with the second end cover 6; it can be seen from Figure 1 and Figure 5 that the sixth boss 12 is provided with a second axial flow channel 27, a third axial flow channel 28, a fourth The axial channel 29 and the fifth axial channel 30, the second axial channel 27, the third axial channel 28, the fourth axial channel 29, the fifth axial channel 30 and the fifth chamber respectively 24 connected. The second chamber 21 is a cavity formed between the second boss 8 and the third boss 9, and the wall of the valve body 1 where the second chamber 21 is located has an oil return port that enables the second chamber 21 to communicate with the oil tank. 36. On the wall of the valve body 1 between the oil return port 36 and the oil drain port 49, there is a seventh axial flow channel 32 that can communicate the second cavity 21 with the first cavity 20; in the seventh axial flow channel 32 internal threads are installed with replaceable variable damping 33. The third chamber 22 is a cavity formed between the third boss 9 and the fourth boss 10, and the wall of the valve body 1 where the third chamber 22 is located has a P inlet that communicates the third chamber 22 with the oil supply system. Oil port 37. The fourth chamber 23 is a cavity formed between the fourth boss 10 and the fifth boss 11, and the wall of the valve body 1 where the fourth chamber 23 is located has an oil return port 38 that communicates the fourth chamber 23 with the oil tank. . The fifth chamber 24 is a cavity formed between the fifth boss 11 and the sixth boss 12, and the wall of the valve body 1 where the fifth chamber 24 is located is provided with a third chamber that communicates the fifth chamber 24 with the oil supply system. The wall of the valve body 1 between the oil port 35 , the third oil port 35 and the second end cover 6 is provided with a sixth axial channel 31 enabling the fifth cavity 24 to communicate with the first axial channel 26 .

As shown in Figure 1, Figure 2 and Figure 5, on the wall of the valve body 1 where the third boss 9 is located, there is an A oil port 39 for controlling the actuator, and on the wall of the valve body 1 of the fourth boss 10 There is a B oil port 40 for controlling the actuator. On one side end surface of the third boss 9, there are first grooves 41 which can make the oil return port 36 communicate with the A oil port 39 at intervals in the circumferential direction, and on the other side end surface of the third boss 9 along the Second grooves 42 are formed at intervals in the circumferential direction to allow the P oil inlet port 37 to communicate with the A oil port 39 . On one side end surface of the fourth boss 10, there are third grooves 43 which can make the P oil inlet 37 communicate with the B oil port 40 at intervals along the circumferential direction, and on the other side end surface of the fourth boss 10 Fourth grooves 44 are formed at intervals along the circumferential direction, enabling the oil return port 38 to communicate with the B oil port 40 .

As shown in Figure 8, the projection of the second groove 42 on the third boss 9 and the third groove 43 on the fourth boss 10 on the projection plane perpendicular to the central axis of the second valve core 4 is along the circumference. The directions are alternately staggered. The projections of the first groove 41 on the third boss 9 and the corresponding second groove 42 on the projection plane perpendicular to the central axis of the second valve core 4 overlap each other, and the third groove on the fourth boss 10 The projections of the groove 43 and the corresponding fourth groove 44 on a projection plane perpendicular to the central axis of the second valve core 4 overlap each other.

As a preferred solution of the present utility model, the first grooves 41 on the third boss 9 are evenly distributed along the circumferential direction of the end surface of the third boss 9, and the second grooves 42 on the third boss 9 are distributed along the circumference of the third boss 9. The circumferential direction of the end surface of the platform 9 is uniformly distributed; the third groove 43 on the fourth boss 10 is evenly distributed along the circumferential direction of the end surface of the fourth boss 10, and the fourth groove 44 on the fourth boss 10 is distributed along the circumferential direction of the fourth boss 10. The four bosses 10 are evenly distributed in the circumferential direction.

As shown in Figures 1 and 3, the valve sleeve 2 is provided with a corresponding first valve sleeve window 45 at the position where the first groove 41 is located, and the valve sleeve 2 is provided with a corresponding window 45 at the position where the second groove 42 is located. The second valve sleeve window 46, the valve sleeve 2 has a corresponding third valve sleeve window 47 at the position where the third groove 43 is located, and the valve sleeve 2 has a corresponding fourth valve sleeve window 47 at the position where the fourth groove 44 is located. Valve sleeve window 48. The projections of the first valve sleeve window 45 on the valve sleeve 2 and the corresponding fourth valve sleeve window 48 on the projection plane perpendicular to the central axis of the second valve core 4 overlap each other, and the second valve sleeve window on the valve sleeve 2 46 and the corresponding third valve sleeve window 47 on the projection plane perpendicular to the central axis of the second valve core 4 overlap each other, the first valve sleeve window 45 on the valve sleeve 2 and the corresponding second valve sleeve window 46 The projections on the projection plane perpendicular to the central axis of the second valve core 4 are alternately staggered along the circumferential direction.

As a preferred solution of the present utility model, the first valve sleeve window 45 on the valve sleeve 2 is evenly distributed along the circumferential direction of the valve sleeve 2, and the second valve sleeve window 46 on the valve sleeve 2 is evenly distributed along the circumferential direction of the valve sleeve 2. distribution, the third valve sleeve windows 47 on the valve sleeve 2 are evenly distributed along the circumferential direction of the valve sleeve 2 , and the fourth valve sleeve windows 48 on the valve sleeve 2 are evenly distributed along the circumferential direction of the valve sleeve 2 .

The reversing working process of the multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve of the utility model is as follows: when the first spool 3 rotates, the spring 17 drives the second spool 4 to rotate. When the second spool 4 rotates to the position shown in Figure 6, the reversing valve of the present invention is in the P→B working state (namely the first working state). At this time, the first groove 41 communicates with the first valve sleeve window 45 , and the third groove communicates with the third valve sleeve window 47 . The hydraulic oil flowing into the third chamber 22 from the P oil inlet 37 passes through the third groove 43 and the third valve sleeve window 47 in the conduction state, and enters the actuator through the B oil port 40; at the same time, the hydraulic oil flowing out from the actuator The hydraulic oil flows through the A oil port 39, and flows into the second chamber 21 through the first groove 41 and the first valve sleeve window 45 in the conduction state, and the hydraulic oil in the second chamber 21 flows back to the oil tank through the oil return port 36 . When the second spool 4 rotates to the position shown in Figure 7, the reversing valve of the present invention is in the P→A working state (that is, the second working state). At this time, the second groove 42 communicates with the second valve sleeve window 46 , and the fourth groove 44 communicates with the fourth valve sleeve window 48 . The hydraulic oil flowing into the third chamber 22 from the P oil inlet 37 passes through the second groove 42 and the second valve sleeve window 46 in the conduction state, and enters the actuator through the A oil port 39; at the same time, the hydraulic oil flowing out from the actuator The hydraulic oil flows through the B oil port 40, and flows into the fourth chamber 23 through the fourth groove 44 and the fourth valve sleeve window 48 in the conduction state, and the hydraulic oil in the fourth chamber 23 flows back to the oil tank through the oil return port 38 . With the rotation of the first spool 3 and the second spool 4, the reversing valve of the utility model is periodically and alternately in the first working state and the second working state, so that the flow area of the four-way reversing valve of the utility model is according to The pattern of big-small-big changes periodically, so that the opening of the valve port changes continuously, realizing the reversing function of the reversing valve of the utility model.

While the first spool 3 and the second spool 4 are rotating, the axial displacement of the second spool 4 can be realized through the following several control methods. As shown in Figure 1, when the sixth axial flow channel 31 and the first axial flow channel 26 remain connected, if the fourth oil port 34 is blocked, the hydraulic oil provided by the oil supply system enters the third oil port 35 Divided into two paths: one of them enters the fifth cavity 24 and passes through the second axial flow channel 27, the third axial flow channel 28, the fourth axial flow channel 29 and the fifth axial flow channel 30, and finally acts on the second axial flow channel The hydraulic power is generated on the bottom surface of the end cover 6; the other way passes through the sixth axial flow channel 31 and the first axial flow channel 26 and enters the axial through hole 25, thereby directly acting on the end surface of the second end 16 of the second valve core generate hydraulic power. At this time, if the variable damper 33 with zero opening is used to block the seventh axial flow passage 32, and make the hydraulic force acting on the end surface of the second end 16 of the second valve core greater than the preset value of the spring 17 force, then the second spool 4 begins to displace axially in the direction where the first spool is located; if the oil drain port 49 is blocked and the variable damper 33 with a fixed opening can be used at the same time, then the second chamber 21 The hydraulic oil enters the first chamber 20 through the seventh axial channel 32; The combined force of the hydrodynamic force of the hydraulic oil, then the second spool 4 begins to displace axially in the direction where the first spool is located. As shown in Figure 9, if the second end cover 6 is rotated 180 degrees, the sixth axial channel 31 and the first axial channel 26 are no longer in communication, when the sixth axial channel 31 and the first axial channel When the flow channel 26 is no longer in communication, the external control hydraulic oil enters the fourth oil port 34 and directly acts on the end surface of the second end 16 of the second valve core through the axial through hole 25 to generate hydraulic force. At this time, if the variable damper 33 with zero opening is used to block the seventh axial channel 32, and make the hydraulic force acting on the end surface of the second end 16 of the second valve core greater than the preset force of the spring 17 , the second spool 4 begins to displace axially in the direction where the first spool is located; if the oil drain port 49 is blocked and the variable damper 33 with a fixed opening is used, then the hydraulic oil in the second chamber 21 Enter the first cavity 20 through the seventh axial channel 32; Then, the second spool 4 begins to displace axially in the direction where the first spool is located.

The content of the implementation statement in this specification is only an enumeration of the realization forms of the utility model concept. The protection scope of the utility model should not be regarded as limited to the specific mode shown in the implementation, but should be related to those skilled in the art according to the utility model. Conceive the equivalent technical methods that can be thought of.

Claims (3)

1. A multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve, comprising a valve body, a valve sleeve, a spool, a first end cap and a second end cap, is characterized in that: the valve The spool is composed of a first spool and a second spool; the first spool is provided with a first boss, and the second spool is provided with a second boss, a third boss, a fourth boss, and a second boss. Five bosses and sixth bosses, first boss, second boss, third boss, fourth boss, fifth boss, sixth boss along the direction from the first end cover to the second end cover arranged sequentially; The first end of the first spool runs through and protrudes from the first end cover, and the first end of the first spool is either connected to the main shaft of the stepper motor through a coupling, or connected to the rotor of the rotary proportional electromagnet; The second end of the first spool is opposite to the first end of the second spool and forms a first cavity between the first boss and the second boss. One chamber communicates with the fuel tank; a spring is arranged in the first chamber, and the second end of the first spool and the first end of the second spool extend into the spring, and one end of the spring is connected to the first end of the second spool. The second spool is fixedly connected, and the other end of the spring is fixedly connected to the first spool; The second end cover is provided with a radial fourth oil port, a first axial flow channel and an axial through hole, the fourth oil port communicates with the first axial flow channel, and the fourth oil port communicates with the first axial flow channel. The axial through hole communicates with each other, and the second end of the second valve core extends into the axial through hole and closely cooperates with each other; The outer end surface of the sixth boss is in close contact with the second end cover, and the sixth boss is provided with a second axial flow channel, a third axial flow channel, a fourth axial flow channel and a fifth axial flow channel , the fifth cavity is formed between the fifth boss and the sixth boss, and the second axial flow channel, the third axial flow channel, the fourth axial flow channel, and the fifth axial flow channel are respectively connected with the fifth cavity In communication, the valve body wall where the fifth chamber is located has a third oil port that communicates the fifth chamber with the oil supply system and a sixth axial flow passage that enables the fifth chamber to communicate with the first axial flow passage; A second chamber is formed between the second boss and the third boss, and the valve body wall where the second chamber is located is provided with a first oil return port that enables the second chamber to communicate with the oil tank and enables the second chamber to communicate with the second chamber. A seventh axial flow passage communicated with one cavity, and variable damping is installed on the internal thread of the seventh axial flow passage; a third cavity is formed between the third boss and the fourth boss, and the valve where the third cavity is located There is a P oil inlet on the body wall that can communicate the third chamber with the oil supply system; a fourth chamber is formed between the fourth boss and the fifth boss, and the wall of the valve body where the fourth chamber is located is opened to allow The second oil return port where the fourth cavity communicates with the fuel tank; A oil port for controlling the actuator is opened on the valve body wall where the third boss is located, and a B oil port for controlling the actuator is opened on the valve body wall where the fourth boss is located; On one end surface of the third boss, there are first grooves that can communicate with the first oil return port and A oil port at intervals along the circumferential direction, and on the other end surface of the third boss at intervals along the circumferential direction. There is a second groove that can connect the P oil inlet with the A oil port; on one end surface of the fourth boss, there are spaced apart along the circumferential direction the first groove that can connect the P oil inlet with the B oil port. Three grooves, on the other end surface of the fourth boss, there are fourth grooves that can communicate with the second oil return port and B oil port at intervals along the circumferential direction; the first groove and the corresponding second groove The projections of the grooves on the projection plane perpendicular to the central axis of the second valve core overlap each other, and the projections of the third groove and the corresponding fourth groove on the projection plane perpendicular to the central axis of the second valve core overlap each other, The projections of the second groove and the third groove on the projection plane perpendicular to the central axis of the second valve core are arranged alternately and staggered along the circumferential direction; The valve sleeve has corresponding first valve sleeve windows, second valve sleeve windows, and third valve sleeve windows at the positions where the first groove, the second groove, the third groove and the fourth groove are located. and the fourth valve sleeve window, the projections of the first valve sleeve window and the corresponding fourth valve sleeve window on the projection plane perpendicular to the central axis of the second valve core overlap each other, and the second valve sleeve window and the corresponding first valve sleeve window The projections of the three valve sleeve windows on the projection plane perpendicular to the central axis of the second valve core overlap each other, and the first valve sleeve window and the second valve sleeve window are on the projection plane perpendicular to the central axis of the second valve core. The projections of are alternately staggered along the circumferential direction. 2. The multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve according to claim 1, characterized in that: the first groove and the second groove are along the third boss The third groove and the fourth groove are evenly distributed along the circumferential direction of the end surface of the fourth boss. 3. The multi-control variable damping dual-degree-of-freedom spool rotary four-way reversing valve according to claim 1 or 2, characterized in that: the first valve sleeve window, the second valve sleeve window, the third The windows of the valve sleeve and the windows of the fourth valve sleeve are evenly distributed along the circumferential direction of the valve sleeve respectively.

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