High-reliability two-stage transmission micro electromagnetic valve

Abstract

This invention discloses a highly reliable two-stage transmission miniature electromagnetic rotary valve, comprising a valve sleeve mounted in a fixed installation position, a valve core disposed within the valve sleeve via a point contact structure, two a-cavities and two b-cavities staggered on the valve core, a connecting hole connecting the two b-cavities on the radial cross-section of the valve core, an annular conductive cavity on the valve core, with both a-cavities communicating with the annular conductive cavity, and a c-cavity centrally symmetrical about the valve sleeve's central axis on the inner wall of the valve sleeve, one end of the valve core extending out of the valve sleeve and connected to a drive unit mounted on a corresponding installation position of the valve sleeve via a two-stage transmission mechanism, the drive unit being a rotational output type power source. This invention solves the problem of excessive radial clamping force between the valve core and the valve sleeve in the prior art, facilitating more stable and reliable rotation of the valve core.

Description

Technical Field

[0001] This invention relates to the technical field of miniature solenoid valves, and in particular to a highly reliable two-stage actuation miniature solenoid rotary valve. Background Technology

[0002] In recent years, the application of miniature solenoid valves in military fields such as aviation, aerospace, and missiles has become increasingly widespread, with increasingly stringent requirements for power density, reliability, high response, and low internal leakage. Currently, commonly used miniature solenoid valves are mainly rotary and direct-drive types. Rotary solenoid valves use an external rotating device to drive the valve core to rotate. The valve core has a channel or cavity. After rotating the valve core, the channel or cavity on the valve core can connect with the output end of the valve sleeve, thereby realizing the conduction of the solenoid valve. Direct-drive solenoid valves use a direct-drive electromagnet to push the valve core to move axially within the valve sleeve. When it moves to the corresponding position, the solenoid valve is activated.

[0003] In some existing conventional rotary solenoid valves, i.e. electromagnetic rotary valves, when high pressure is introduced into the through hole at one end of the valve sleeve, the high pressure will exert a pressing force on the valve core, pushing the valve core to press against the valve sleeve end cover. At the same time, it will also make the valve core press very tightly against the inner wall of the valve sleeve. The radial clamping force of the valve core will be very large. When the valve core is rotated by an external rotating device, it is necessary to overcome the large radial clamping force, which makes it inconvenient for the valve core to rotate. Summary of the Invention

[0004] To address the shortcomings in the aforementioned background technology, this invention proposes a highly reliable two-stage transmission miniature electromagnetic rotary valve, which solves the problem of excessive radial clamping force between the valve core and valve sleeve in the prior art, and facilitates more stable and reliable rotation of the valve core.

[0005] The technical solution of this invention is implemented as follows:

[0006] A highly reliable two-stage transmission miniature electromagnetic rotary valve includes a valve sleeve mounted in a fixed installation position. A valve core is installed inside the valve sleeve via a point contact structure. Two a-cavities and two b-cavities are staggered on the valve core. A connecting hole connecting the two b-cavities is opened on the radial cross section of the valve core. An annular conductive cavity is opened on the valve core, and both a-cavities communicate with the annular conductive cavity. A c-cavity is centrally symmetrical about the central axis of the valve sleeve. One end of the valve core extends out of the valve sleeve and is connected to a drive unit mounted in a relatively opposite installation position on the valve sleeve through a two-stage transmission mechanism. The drive unit is a rotational output type power source.

[0007] Furthermore, the point contact structure includes a valve sleeve plug, a spherical limiting plug, a limiting return spring, and a thrust ball bearing. The valve sleeve plug is located at the valve sleeve port and at one end of the valve core. The spherical limiting plug is located at the end of the valve sleeve plug near the valve core via the limiting return spring. The valve sleeve plug has an inner hole that communicates with the c-cavity. The ball end of the spherical limiting plug faces the valve core and contacts it. An integrally formed pressure ring is provided on the valve core. The thrust ball bearing is sleeved on the valve core and located on the side of the pressure ring away from the spherical limiting plug. A limiting retaining ring is provided on the side of the thrust ball bearing away from the pressure ring to prevent the thrust ball bearing from disengaging from the valve sleeve.

[0008] Furthermore, the valve sleeve is provided with a pressure inlet P communicating with cavity a and an oil return port O communicating with cavity b. The end of the valve sleeve near the valve sleeve plug is set as the working port A. The working port A, the valve sleeve plug and the spherical limiting plug are coaxially arranged, and the working port A communicates with the inner hole of the valve sleeve plug.

[0009] When the pressure inlet P is under high pressure and the drive unit does not drive the valve core to rotate, chamber b is connected to chamber c, chamber a is cut off from chamber c, the pressure inlet P is cut off from working port A and return port O, and working port A and return port O are connected to form a low-pressure flow channel.

[0010] When the pressure inlet P is supplied with high pressure and the drive unit drives the valve core to rotate, chamber a and chamber c are connected, chamber b and chamber c are cut off, the oil return port O is cut off from the working port A and the pressure inlet P, and the working port A and the pressure inlet P are connected to form a high-pressure flow channel.

[0011] Furthermore, the secondary transmission mechanism includes a main lever, a secondary lever, a shift fork, and a circumferential retaining spring. The end cover of the drive unit is provided with corresponding left and right pin seats, and a pin shaft is provided between the left and right pin seats. The circumferential retaining spring is mounted on the pin shaft, with one end connected to the left pin seat and the other end connected to a spring retaining ring sleeved on the pin shaft. The shift fork is located at the rotation output end of the drive unit, with one end extending between the right pin seat and the spring retaining ring and movably connected to the pin shaft. The main lever is rotatably mounted on the end cover of the drive unit and is located on the side of the rotation output end of the drive unit away from the pin shaft. The end of the main lever near the pin shaft is connected to the end of the shift fork away from the pin shaft, and the other end is connected to the secondary lever mounted on the valve core through a linkage assembly.

[0012] Furthermore, the end of the shift fork furthest from the pin is the larger end, and the end of the main lever facing the shift fork is a U-shaped port. The larger end of the shift fork is inserted into the U-shaped port of the main lever and connected with the main lever.

[0013] Furthermore, the linkage assembly includes a linkage port opened at the end of the main lever away from the shift fork and a drive shaft disposed on the secondary lever. The drive shaft is located at the end of the secondary lever, and the linkage port is an irregularly shaped port. The drive shaft corresponds and matches the linkage port. The drive shaft is inserted into the corresponding linkage port, and when the main lever rotates, it can drive the drive shaft to move through the linkage port.

[0014] Furthermore, the end of the shift fork extending to the pin has a slot, through which the pin passes. The slot allows the end of the shift fork facing the pin to move along the pin without disengaging from it.

[0015] Furthermore, the end of the shift fork extending to the pin is always in contact with the spring retaining ring.

[0016] Furthermore, the driving unit is a servo motor, a stepper motor, or a rotary electromagnet.

[0017] Furthermore, a sealing ring is provided between the valve core and the valve sleeve to prevent hydraulic oil from flowing to the thrust ball bearing.

[0018] The beneficial technical effects of this invention are as follows:

[0019] 1. When the two a chambers and two b chambers are staggered and supplied with high pressure or low pressure, the radial force on the valve core in the valve sleeve is balanced. The radial clamping force on the valve core in the valve sleeve is smaller when the forces are balanced, which makes it easier for the valve core to rotate in the valve sleeve.

[0020] 2. When high pressure is applied to chamber a or b, the high pressure load can cause the end of the valve core away from the valve sleeve plug to be pressed against the thrust ball bearing. At the same time, the spherical limit plug is pressed against the end of the valve core near the valve sleeve plug under the action of the limit return spring. When the valve core is rotated, one end of the valve core is subjected to the rolling friction of the thrust ball bearing, and the other end is subjected to the point-to-surface friction between the valve core and the spherical limit plug. Both friction forces are very small. Compared with the traditional electromagnetic rotary valve, the rotation damping of the valve core is reduced, making it easier for the valve core to rotate in the valve sleeve.

[0021] 3. The limit return spring can exert a certain pressure on the spherical limit plug, thereby ensuring that the pressure ring on the valve core is always pressed against the thrust ball bearing, preventing the steel balls inside the thrust ball bearing from falling out.

[0022] 4. When the output end of the drive unit rotates, it can drive the shift fork to rotate. The rotation of the shift fork can compress the circumferential holding spring. At the same time, the large end of the shift fork can drive the main shift rod to move through the U-shaped port on the main shift rod. The main shift rod drives the auxiliary shift rod to rotate through the linkage assembly, thereby driving the valve core to rotate. This realizes the transmission of the valve core by the rotating electromagnet in the axial direction of the valve core. This allows the present invention to be applied to application scenarios where the requirements in the direction perpendicular to the axial direction of the valve core are high, while the requirements in the axial direction of the valve core are low.

[0023] 5. When the drive unit is not in operation, the restoring force of the circumferential retaining spring can drive the shift fork to return to its initial position, thereby driving the main shift lever to return, so that the auxiliary shift lever and valve core can rotate to their initial state.

[0024] 6. A first-stage transmission is formed between the shift fork and the main shift lever, and a second-stage transmission is formed between the main shift lever and the auxiliary shift lever. This allows the drive unit to drive the valve core to rotate through the two-stage transmission mechanism. The two-stage transmission mechanism can amplify the torque transmitted by the valve core, which can greatly improve the reliability of the present invention. Attached Figure Description

[0025] To more clearly illustrate the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0026] Figure 1 This is a schematic diagram of the overall cross-sectional structure of the present invention;

[0027] Figure 2 for Figure 1 An enlarged schematic diagram of part A in the middle;

[0028] Figure 3 This is a schematic diagram of the cross-sectional structure of chambers a and b of the valve core;

[0029] Figure 4 This is a schematic diagram of the secondary transmission mechanism at the end cover of the drive unit;

[0030] Figure 5 This is a schematic diagram of the structure between the pin and the left and right pin seats at the end cover of the drive unit.

[0031] In the diagram, 1. Valve sleeve; 2. Valve core; 21. Pressure ring; 3. Point contact structure; 31. Valve sleeve plug; 32. Spherical limit plug; 33. Limit return spring; 34. Thrust ball bearing; 321. Shoulder plate; 322. Ball end; 41. Chamber a; 42. Chamber b; 43. Connecting hole; 44. Annular conducting cavity; 11. Chamber c; 5. Secondary transmission mechanism; 6. Drive unit; 51. Main lever; 52. Secondary lever; 53. Shift fork; 54. Circumferential retaining spring; 61. Left pin seat; 62. Right pin seat; 63. Pin shaft; 64. Spring retaining ring; 7. Linkage assembly; 71. Linkage port; 72. Drive shaft; 12. Sealing groove; 13. Sealing ring. Detailed Implementation

[0032] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0033] Example 1:

[0034] As shown in the figure, a highly reliable two-stage transmission miniature electromagnetic rotary valve includes a valve sleeve 1 mounted in a fixed position. The inner bore of the valve sleeve 1 is a T-shaped bore, comprising a wide section and a narrow section. A valve core 2 is disposed within the inner bore of the valve sleeve 1, and the valve core 2 is installed within the valve sleeve 1 via a point contact structure 3.

[0035] One end of the valve core 2 is inserted into the narrow hole, and the other end passes through the wide hole and extends out of the valve sleeve 1. The valve core 2 is provided with an integrally formed pressure ring 21. The plane direction of the pressure ring 21 is perpendicular to the length direction of the valve core 2. The pressure ring 21 is located in the wide hole of the inner hole of the valve sleeve 1 and close to the narrow hole of the valve sleeve 1.

[0036] The point contact structure 3 includes a valve sleeve plug 31, a spherical limiting plug 32, a limiting return spring 33, and a thrust ball bearing 34. The valve sleeve plug 31 is installed at the port inside the valve sleeve 1 and is located at one end of the valve core 2. The valve sleeve plug 31 has an inner hole that corresponds to and communicates with the port of the valve sleeve 1. The spherical limiting plug 32 is located at the end of the valve sleeve plug 31 near the valve core 2 via the limiting return spring 33.

[0037] The spherical limit plug 32 includes a shoulder plate 321 and a ball end 322. The limit return spring 33 is a spring, with one end fixedly connected to the end of the valve sleeve plug 31 and the other end fixedly connected to the shoulder plate 321 of the spherical limit plug 32. The ball end 322 of the spherical limit plug 32 is fixed to the side of the shoulder plate 321 away from the limit return spring 33, and the spherical limit plug 32 is pressed against the valve core 2 under the elastic force of the limit return spring 33.

[0038] The ball-shaped limiting plug 32 and the valve core 2 are in point contact, and the friction between them is the friction between a point and a surface. Although the thrust ball bearing 34 and the valve core 2 are in surface contact, the thrust ball bearing 34 is only subjected to rolling friction when rotating. This is much smaller than the sliding friction between the conventional valve core 2 and the end cover of the valve sleeve 1. The point contact structure 3 can reduce the rotational damping of the valve core 2 and make it easier for the valve core 2 to rotate in the valve sleeve 1.

[0039] The thrust ball bearing 34 is sleeved on the valve core 2 and disposed in the wide part of the inner hole of the valve sleeve 1. The thrust ball bearing 34 is located on the side of the pressure ring 21 away from the narrow part of the hole. A limiting ring is provided on the side of the thrust ball bearing 34 away from the pressure ring 21 to prevent the thrust ball bearing 34 from dislodging from the wide part of the hole.

[0040] The valve core 2 has two staggered a-cavities 41 and two b-cavities 42, with the b-cavities 42 not communicating with the a-cavities 41. The two a-cavities 41 and two b-cavities 42 are centrally symmetrical about the central axis of the valve core 2. A connecting hole 43 is formed in the radial section of the valve core 2, connecting the two b-cavities 42. The length direction of the line connecting the centers of the two a-cavities 41 is perpendicular to the length direction of the connecting hole 43. An annular conductive cavity 44 is formed on the valve core 2, and both a-cavities 41 communicate with the annular conductive cavity 44.

[0041] Since the two staggered chambers a41 and two chambers b42 are centrally symmetrical about the central axis of the valve core 2, the radial force on the valve core 2 within the valve sleeve 1 is balanced regardless of whether high pressure is applied to chamber a41 or chamber b42. When the radial force on the valve core 2 within the valve sleeve 1 is balanced, the radial clamping force on the valve core 2 is very small, making it easier for the valve core 2 to rotate within the valve sleeve 1.

[0042] Two centrally symmetrical c-cavities 11 about the central axis of the valve sleeve 1 are formed on the inner wall of the valve sleeve 1. Both c-cavities 11 communicate with the inner hole of the valve sleeve plug 31. The end of the valve core 2 away from the valve sleeve plug 31 extends out of the valve sleeve 1 and is connected to the drive unit 6, which is installed opposite to the valve sleeve 1, through a secondary transmission mechanism 5. The drive unit 6 is a rotational output type power source, and the rotational output shaft of the drive unit 6 can drive the valve core 2 to rotate inside the valve sleeve 1 through the secondary transmission mechanism 5.

[0043] The valve sleeve 1 has a pressure inlet P communicating with cavity a 41 and an oil return port O communicating with cavity b 42. The end of the valve sleeve 1 near the valve sleeve plug 31 is set as the working port A. The working port A, the valve sleeve plug 31 and the spherical limit plug 32 are arranged coaxially.

[0044] When the P port is under high pressure and the drive unit 6 does not drive the valve core 2 to rotate through the secondary transmission mechanism 5, the b chamber 42 is connected to the c chamber 11, the a chamber 41 is cut off from the c chamber 11, the pressure inlet P is cut off from the working port A and the return port O, and the working port A and the return port O are connected to form a low-pressure flow channel.

[0045] When the pressure inlet P is supplied with high pressure and the drive unit 6 drives the valve core 2 to rotate through the secondary transmission mechanism 5, chamber a 41 is connected to chamber c 11, chamber b 42 is cut off from chamber c 11, the oil return port O is cut off from the working port A and the pressure inlet P, and the working port A and the pressure inlet P are connected to form a high-pressure flow channel.

[0046] The secondary transmission mechanism 5 includes a main lever 51, a secondary lever 52, a lever fork 53, and a circumferential retaining spring 54. The drive unit 6 is coaxially mounted with the valve core 2 at a position opposite to the valve sleeve 1. A left pin seat 61 and a right pin seat 62, corresponding to each other, are fixed to the end cap of the drive unit 6 facing the valve core 2, with a pin 63 positioned between them. The circumferential retaining spring 54 is sleeved on the pin 63, with one end connected to the left pin seat 61 and the other end connected to a spring retaining ring 64 sleeved on the pin 63.

[0047] A shift fork 53 is located at the rotation output end of the drive unit 6. One end of the shift fork 53 extends between the right pin seat 62 and the spring retaining ring 64, and is always in contact with the spring retaining ring 64. The end of the shift fork 53 extending to the pin 63 has a slot, through which the pin 63 passes. This slot allows the end of the shift fork 53 facing the pin 63 to move along the pin 63 without disengaging from it, thus achieving a movable connection between the shift fork 53 and the pin 63. The circumferential retaining spring 54 has a certain restoring capability to the spring retaining ring 64. When the drive unit 6 no longer provides power to rotate the shift fork 53, the circumferential retaining spring 54 can provide a certain restoring effect to the shift fork 53 through the spring retaining ring 64.

[0048] The main lever 51 is rotatably mounted on the end cap on one side of the output end of the drive unit 6. The main lever 51 is located on the side of the drive unit 6 away from the rotating output end away from the pin 63. The end of the main lever 51 facing the shift fork 53 is a U-shaped port, and the end of the shift fork 53 away from the pin 63 is a large end. The large end of the shift fork 53 is inserted into the U-shaped port of the main lever 51 and contacts the inner wall of the U-shaped port, thereby realizing the mating connection between the shift fork 53 and the main lever 51.

[0049] The auxiliary lever 52 is fixed to the end of the valve core 2 extending out of the valve sleeve 1, and is perpendicular to the valve core 2. The end of the main lever 51 away from the shift fork 53 is connected to the auxiliary lever 52 via a linkage assembly 7. The linkage assembly 7 includes a linkage port 71 at the end of the main lever 51 away from the shift fork 53 and a drive shaft 72 mounted on the auxiliary lever 52. The drive shaft 72 is axially parallel to the valve core 2 and is located at the end of the auxiliary lever 52. The linkage port 71 is an irregularly shaped port, and the drive shaft 72 corresponds to and matches the linkage port 71. The end of the drive shaft 72 away from the auxiliary lever 52 is inserted into the corresponding linkage port 71. When the main lever 51 rotates, it can drive the drive shaft 72 to rotate around the central axis of the valve core 2 through the linkage port 71.

[0050] In this invention, since the two a chambers 41 and the two b chambers 42 are symmetrically arranged, the radial force on the valve core 2 is balanced regardless of whether the a chamber 41 or the b chamber 42 is under high pressure. This results in a very small radial clamping force on the valve core 2, making it easier for the valve core 2 to rotate. At the same time, the spherical limit plug 32 and the thrust ball bearing 34 further reduce the friction force that the valve core 2 needs to overcome to rotate within the valve sleeve 1, making the rotation of the valve core 2 even easier.

[0051] When high voltage is applied to port P, and the drive unit 6 drives the shift fork 53 to move, a first-stage transmission is formed between the shift fork 53 and the main shift lever 51, and a second-stage transmission is formed between the main shift lever 51 and the auxiliary shift lever 52. This causes the drive unit 6 to drive the valve core 2 to rotate through the two-stage transmission mechanism. The two-stage transmission mechanism can amplify the transmission ratio of the valve core 2, thereby amplifying the transmitted torque and greatly improving the rotation reliability of the valve core 2.

[0052] When high voltage is applied to port P and drive unit 6 is not working, the restoring force of circumferential retaining spring 54 is amplified through shift fork 53 and shift rod and then transmitted to valve core 2, causing valve core 2 to rotate back to its initial state.

[0053] The aforementioned mechanical structure for transmitting torque and force is simple, reliable, and highly efficient, ensuring the normal rotation of the valve core 2 and improving the reliability of the invention.

[0054] Example 2:

[0055] This embodiment is a further improvement based on Embodiment 1. In this embodiment, the drive unit 6 is selected as a servo motor, a stepper motor, or a rotary electromagnet. Servo motors and stepper motors are more convenient for operators to control the speed and direction, while rotary electromagnets have the characteristics of fixed rotation amplitude and automatic return, all of which can meet the requirements of the present invention for the drive unit 6.

[0056] In addition, in this embodiment, a sealing groove 12 is provided on the narrow hole wall of the valve sleeve 1, and a sealing ring 13 is provided in the sealing groove 12 and fitted on the valve core 2. The sealing ring 13 abuts against the bottom of the sealing groove 12, and the sealing ring 13 can prevent the high pressure oil at port A from flowing to the thrust ball bearing 34, thus avoiding greater oil resistance when the thrust ball bearing 34 rotates, and making it easier for the valve core 2 to rotate in the valve sleeve 1.

[0057] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A highly reliable two-stage actuated miniature electromagnetic rotary valve, comprising a valve sleeve disposed in a fixed mounting position, characterized in that: The valve core is provided inside the valve sleeve through a point contact structure. Two a-cavities and two b-cavities are staggered on the valve core. A connecting hole connecting the two b-cavities is opened on the radial section of the valve core. An annular conducting cavity is opened on the valve core. Both a-cavities are connected to the annular conducting cavity. A c-cavity is opened on the inner wall of the valve sleeve in a centrally symmetrical manner about the central axis of the valve sleeve. One end of the valve core extends out of the valve sleeve and is connected to the drive unit set at the opposite installation position of the valve sleeve through a two-stage transmission mechanism. The drive unit is a rotation output type power source. The point contact structure includes a valve sleeve plug, a spherical limiting plug, a limiting return spring, and a thrust ball bearing. The valve sleeve plug is located at the valve sleeve port and at one end of the valve core. The spherical limiting plug is located at the end of the valve sleeve plug near the valve core via the limiting return spring. The valve sleeve plug has an inner hole that communicates with the c-cavity. The ball end of the spherical limiting plug faces the valve core and contacts it. The valve core has an integrally formed pressure ring. The thrust ball bearing is sleeved on the valve core and located on the side of the pressure ring away from the spherical limiting plug. A limiting retaining ring is provided on the side of the thrust ball bearing away from the pressure ring to prevent the thrust ball bearing from disengaging from the valve sleeve. The valve sleeve has an inlet port P communicating with cavity a and an outlet port O communicating with cavity b. The end of the valve sleeve near the valve sleeve plug is set as the working port A. The working port A, the valve sleeve plug and the spherical limiting plug are coaxially arranged, and the working port A communicates with the inner hole of the valve sleeve plug. When the inlet port P is supplied with high pressure and the drive unit does not drive the valve core to rotate, cavity b communicates with cavity c, cavity a is cut off from cavity c, and the inlet port P is cut off from working port A and outlet port O. Working port A and outlet port O are connected to form a low-pressure flow channel. When the inlet port P is supplied with high pressure and the drive unit drives the valve core to rotate, cavity a communicates with cavity c, cavity b is cut off from cavity c, and outlet port O is cut off from working port A and inlet port P. Working port A and inlet port P are connected to form a high-pressure flow channel. The secondary transmission mechanism includes a main lever, a secondary lever, a shift fork, and a circumferential retaining spring. The end cover of the drive unit is provided with corresponding left and right pin seats. A pin shaft is provided between the left and right pin seats. The circumferential retaining spring is mounted on the pin shaft, with one end connected to the left pin seat and the other end connected to a spring retaining ring sleeved on the pin shaft. The shift fork is located at the rotation output end of the drive unit. One end of the shift fork extends between the right pin seat and the spring retaining ring and is movably connected to the pin shaft. The main lever is rotatably mounted on the end cover of the drive unit and is located on the side of the rotation output end of the drive unit away from the pin shaft. The end of the main lever near the pin shaft is connected to the end of the shift fork away from the pin shaft, and the other end is connected to the secondary lever mounted on the valve core through a linkage assembly.

2. The highly reliable two-stage transmission miniature electromagnetic rotary valve according to claim 1, characterized in that: The end of the shift fork furthest from the pin is the large end, and the end of the main lever facing the shift fork is a U-shaped port. The large end of the shift fork is inserted into the U-shaped port of the main lever and connected with the main lever.

3. The highly reliable two-stage transmission miniature electromagnetic rotary valve according to claim 2, characterized in that: The linkage assembly includes a linkage port opened at the end of the main lever away from the shift fork and a drive shaft disposed on the secondary lever. The drive shaft is located at the end of the secondary lever, and the linkage port is an irregularly shaped port. The drive shaft corresponds to and matches the linkage port. The drive shaft is inserted into the corresponding linkage port, and when the main lever rotates, it can drive the drive shaft to move through the linkage port.

4. A highly reliable two-stage transmission miniature electromagnetic rotary valve according to claim 2 or 3, characterized in that: The fork extends to one end of the pin and has a slot, through which the pin passes. The slot allows the fork to move along the pin without disengaging from it.

5. A highly reliable two-stage transmission miniature electromagnetic rotary valve according to claim 4, characterized in that: The end of the shift fork extending to the pin is always in contact with the spring retaining ring.

6. A highly reliable two-stage transmission miniature electromagnetic rotary valve according to any one of claims 1-3 and 5, characterized in that: The drive unit is a servo motor, a stepper motor, or a rotary electromagnet.

7. A highly reliable two-stage transmission miniature electromagnetic rotary valve according to claim 6, characterized in that: A sealing ring is provided between the valve core and the valve sleeve to prevent hydraulic oil from flowing to the thrust ball bearing.

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