CN118361425A - Rotatory tee bend pressure servo valve that directly drives - Google Patents

Abstract

A rotary direct-drive three-way pressure servo valve relates to the technical field of electrohydraulic servo valves. The invention solves the problems of large volume, complex structure, large internal leakage, high processing and maintenance cost and the like of the traditional pressure servo valve, and further provides a rotary direct-drive three-way pressure servo valve. The valve sleeve is sleeved on the lower part of a valve core, the sealing cover is arranged on the upper part of the valve core, the lower end of the sealing cover is fixedly connected with the upper end of the valve sleeve, the valve body is sleeved on the upper part of the valve sleeve, the lower end of the valve body is connected with the upper end of the valve sleeve through threads, a sensor end cover is arranged above the valve body, a fixing flange is arranged between the sensor end cover and the valve body, a magnet fixing seat is arranged at the upper end of the valve core, a motor rotor magnet is arranged between the valve core and the sealing cover, a motor stator is arranged between the sealing cover and the valve body, the magnet is arranged on the magnet fixing seat, and a magnetic angle sensor module is arranged between the fixing flange and the sensor end cover. The invention has simple structure, easy processing and assembly, high control linearity, higher success and high pollution resistance.

Description

A rotary direct-drive three-way pressure servo valve

Technical Field

The invention relates to the technical field of electro-hydraulic servo valves, and in particular to a rotary direct-drive three-way pressure servo valve.

Background technique

As a key component in hydraulic control systems, the pressure servo valve is a hydraulic control valve that converts electrical signals into load port output pressure. It has the advantages of low leakage, fast response, and high control accuracy, and is widely used in brake systems, robots, and other fields. However, the traditional pressure servo valve uses nozzle baffle and jet tube as the servo valve pilot stage, and uses pressure negative feedback to achieve pressure regulation. It has defects such as large size, complex structure, large internal leakage, and high processing and maintenance costs, which limits its application in scenarios with high energy efficiency and high frequency response.

Summary of the invention

The purpose of the present invention is to solve the problems of existing pressure servo valves, such as large volume, complex structure, large internal leakage, high processing and maintenance costs, and further provide a rotary direct-drive three-way pressure servo valve.

The technical solution of the present invention is:

A rotary direct-drive three-way pressure servo valve, comprising a main rotary valve subassembly 1, a valve core drive motor assembly 2 and a system sensing module 3, wherein the main rotary valve subassembly 1 comprises a valve sleeve 101, a valve core 102, a sealing cover 107, a valve body 109, a fixing flange 113, a sensor end cover 114 and a magnet fixing seat 110, wherein the valve sleeve 101 is sleeved on the lower part of the valve core 102, the sealing cover 107 is sleeved on the upper part of the valve core 102, the lower end of the sealing cover 107 is fixedly connected to the upper end of the valve sleeve 101, the valve body 109 is sleeved on the upper part of the valve sleeve 101, the lower end of the valve body 109 is connected to the upper end of the valve sleeve 101 by threads, a sensor end cover 114 is arranged above the valve body 109, a fixing flange 113 is arranged between the sensor end cover 114 and the valve body 109, the sensor end cover 114, the fixing flange 113 and the valve body 109 are fixedly connected by a first connecting element 112, and the upper end of the valve core 102 is provided with a magnet fixing seat 110. 10. The valve core drive motor assembly 2 includes a motor stator 201 and a motor rotor magnet 202. A motor rotor magnet 202 is provided between the valve core 102 and the sealing cover 107. The motor stator 201 is sleeved on the upper end of the valve core 102. A motor stator 201 is provided between the sealing cover 107 and the valve body 109. The motor stator 201 is sleeved in the middle of the sealing cover 107. The motor stator 201 and the motor rotor magnet 202 are arranged correspondingly; the system sensing module 3 includes a magnet 301, a magnetic angle sensor module 302 and a servo valve cable 303. The magnet 301 is installed on the magnet fixing seat 110. A magnetic angle sensor module 302 is provided between the fixing flange 113 and the sensor end cover 114. The magnetic angle sensor module 302 and the fixing flange 113 are fixedly connected by the second connecting element 104. One end of the servo valve cable 303 is connected to the magnetic angle sensor module 302.

Furthermore, the main rotary valve subassembly 1 further includes two silicon steel sheets 108 , which are respectively arranged on the upper and lower sides of the motor stator 201 , and the silicon steel sheets 108 are coaxially arranged with the motor stator 201 .

Furthermore, the main rotary valve sub-assembly 1 also includes a wire passing ring 115, and an axially arranged wire passing ring assembly through hole is opened at the upper end of the sensor end cover 114. The wire passing ring 115 is installed in the wire passing ring assembly through hole, and the other end of the servo valve cable 303 passes through the wire passing ring 115 and extends to the outside. The servo valve cable 303 is fixed to the sensor end cover 114 through the wire passing ring 115.

Furthermore, the magnet fixing seat 110 is a columnar structure with a T-shaped cross-section. A fixing seat assembly countersunk hole is axially opened at the center of the upper end surface of the valve core 102. The lower end of the magnet fixing seat 110 is inserted into the fixing seat assembly countersunk hole. A magnet assembly groove is opened at the center of the upper surface of the magnet fixing seat 110, and the magnet 301 is installed in the magnet assembly groove.

Furthermore, the valve core 102 and the valve sleeve 101 divide the oil circuit into P oil chamber 402, T oil chamber 404, A oil chamber 403 and B oil chamber 401. When the motor stator 201 drives the valve core 102 to perform radial rotation in the valve sleeve 101, the throttle port and flow groove provided on the valve core 102 and the valve sleeve 101 can realize the connection and switching between the A oil chamber 403, the B oil chamber 401, the P oil chamber 402 and the T oil chamber 404, so that it has a three-position four-way function.

Furthermore, the valve sleeve 101 is an annular structure, and four pairs of shaft shoulders are provided on the valve sleeve 101, and the four pairs of shaft shoulders isolate three oil chambers from the valve sleeve 101, which are respectively the B oil chamber 401, the P oil chamber 402 and the A oil chamber 403 from top to bottom, the P oil chamber 402 is connected to the oil outlet pipeline, and the A oil chamber 403 and the B oil chamber 401 are respectively connected to two oil circuits of the load;

The A oil chamber 403 of the valve sleeve 101 is provided with a first throttle port A1 and a second throttle port A2 arranged in a circumferentially symmetrical manner;

The oil chamber B 401 of the valve sleeve 101 is provided with a third throttle port B1 and a fourth throttle port B2 which are arranged symmetrically in a circumference;

The P oil chamber 402 of the valve sleeve 101 is provided with a first oil outlet P1 and a second oil outlet P2 which are arranged in a circumferentially symmetrical manner.

Furthermore, the valve core 102 is a hollow structure, and a T oil chamber 404 is provided inside the valve core 102, and the T oil chamber 404 is connected to the oil return pipeline;

The valve core 102 is provided with a first flow groove C1 and a second flow groove C2 arranged symmetrically in a circumference, and one end of the first flow groove C1 and the second flow groove C2 are connected to the P oil chamber 402 through the first oil outlet P1 and the second oil outlet P2 respectively;

The valve core 102 is provided with a fifth throttle port D1 and a sixth throttle port D2 which are arranged symmetrically in a circumference, and both the fifth throttle port D1 and the sixth throttle port D2 are communicated with the T oil chamber 404 .

Furthermore, the valve core 102 performs radial rotational motion in the valve sleeve 101. When the valve core 102 rotates a certain angle, the fifth throttle port D1 on the valve core 102 coincides with the third throttle port B1 of the B oil chamber 401 on the valve sleeve 101, so that the B oil chamber 401 communicates with the T oil chamber 404. At the same time, the other end of the first flow groove C1 on the valve core 102 coincides with the first throttle port A1 of the A oil chamber 403 on the valve sleeve 101, so that the A oil chamber 403 communicates with the P oil chamber 402. At this time, the load moves in one direction, and the speed of the movement is determined by the degree of position overlap.

The first flow groove C1 and the fifth throttle port D1 are aligned in the axial direction, and the first throttle port A1 and the third throttle port B1 are aligned in the axial direction, which can ensure that the oil outlet and the oil return paths have the same overlap at the throttle ports.

Furthermore, the valve core 102 performs radial rotational motion in the valve sleeve 101. When the valve core 102 rotates a certain angle, the sixth throttle port D2 on the valve core 102 coincides with the first throttle port A1 of the A oil chamber 403 on the valve sleeve 101, so that the A oil chamber 403 communicates with the T oil chamber 404. At the same time, the other end of the second flow groove C2 on the valve core 102 coincides with the fourth throttle port B2 of the B oil chamber 401 on the valve sleeve 101, so that the B oil chamber 401 communicates with the P oil chamber 402. At this time, the load moves in the opposite direction, and the speed of the movement is determined by the degree of position overlap.

The second flow groove C2 and the sixth throttle port D2 are aligned in the axial direction, and the second throttle port A2 and the fourth throttle port B2 are aligned in the axial direction, which can ensure that the oil outlet and the oil return paths have the same degree of overlap at the throttle ports.

Furthermore, the valve core 102 performs radial rotational motion in the valve sleeve 101. When the valve core 102 rotates a certain angle, the fifth throttle port D1 and the sixth throttle port D2 on the valve core 102 do not overlap with the first throttle port A1 and the second throttle port A2 of the A oil chamber 403 on the valve sleeve 101 and the third throttle port B1 and the fourth throttle port B2 of the B oil chamber 401 on the valve sleeve 101, so that the A oil chamber 403 and the B oil chamber 401 are not overlapped. 01 is not connected to T oil chamber 404, and at the same time, the other ends of the first flow groove C1 and the second flow groove C2 on the valve core 102 do not coincide with the first throttle port A1 and the second throttle port A2 of the A oil chamber 403 on the valve sleeve 101 and the third throttle port B1 and the fourth throttle port B2 of the B oil chamber 401 on the valve sleeve 101, so that the A oil chamber 403, the B oil chamber 401 and the P oil chamber 402 are not connected, and the servo valve is in the middle position.

Compared with the prior art, the present invention has the following effects:

1. The present invention adopts a screw-in cartridge valve structure design, the valve body assembly has fewer parts, the motor rotor and the valve core are designed as one body, and it has the advantages of small size, compact structure, simple assembly, and high degree of integration.

2. The present invention uses a first sealing ring to achieve sealing between the valve core, the valve sleeve and the valve body, without dynamic sealing, thus avoiding leakage. At the same time, the radial friction force when the valve core rotates is greatly reduced, thereby improving the energy efficiency of the servo valve.

3. The present invention adopts a rotary valve core design, and drives the valve core to rotate relative to the valve sleeve through the motor rotor, so as to realize the on-off and switching between the load chamber and the P oil chamber and the T oil chamber, so that it has a three-position two-way function. By controlling the rotation angle of the valve core to control the overlap degree of the throttle port on the valve core and the valve sleeve, precise control of pressure is achieved, thereby improving the pressure control accuracy of the servo valve.

4. The present invention is designed with a throttle port and an oil outlet arranged in a circumferentially symmetrical manner on the valve sleeve, and a throttle port and a flow groove arranged in a circumferentially symmetrical manner on the valve core, and the throttle port and the flow groove are aligned in an orderly manner in the axial direction, so as to achieve hydraulic balance when the valve core rotates and reduce the rotational resistance of the motor rotor.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is an isometric view of a rotary direct-drive three-way pressure servo valve of the present invention;

FIG2 is an assembly diagram of a rotary direct-drive three-way pressure servo valve of the present invention;

FIG3 is an assembly diagram of a valve body assembly of a rotary direct-drive three-way pressure servo valve of the present invention;

FIG4 is an assembly diagram of a motor assembly of a rotary direct-drive three-way pressure servo valve of the present invention;

FIG5 is an assembly diagram of a system sensing module of a rotary direct-drive three-way pressure servo valve of the present invention;

FIG6 is a schematic structural diagram of a rotary direct-drive three-way pressure servo valve of the present invention;

7 is an expanded view of the structure of the cylindrical portion of the valve sleeve of a rotary direct-drive three-way pressure servo valve of the present invention;

8 is an expanded view of the valve core cylindrical portion structure of a rotary direct-drive three-way pressure servo valve of the present invention;

9 is a schematic diagram of a rotary direct-drive three-way pressure servo valve in a first working state according to the present invention;

10 is a schematic diagram of a rotary direct-drive three-way pressure servo valve of the present invention in a second working state;

FIG. 11 is a schematic diagram of a rotary direct-drive three-way pressure servo valve in a neutral position according to the present invention.

In the figure: 1 is the main rotary valve subassembly; 2 is the valve core drive motor assembly; 3 is the system sensing module; 101 is the valve sleeve; 102 is the valve core; 103 is the first sealing ring; 104 is the second connecting element; 105 is the first bearing; 106 is the second bearing; 107 is the sealing cover; 108 is the silicon steel sheet; 109 is the valve body; 110 is the magnet fixing seat; 111 is the second sealing ring; 112 is the first connecting element; 113 is the fixing flange; 114 is the sensor end cover; 115 is Wire ring; 201 is the motor stator; 202 is the motor rotor magnet; 301 is the magnet; 302 is the magnetic angle sensor module; 303 is the servo valve cable; B oil chamber 401; P oil chamber 402; A oil chamber 403; T oil chamber 404; the first throttle port A1; the second throttle port A2; the third throttle port B1; the fourth throttle port B2; the first oil outlet P1; the second oil outlet P2; the first circulation groove C1; the second circulation groove C2; the fifth throttle port D1; the sixth throttle port D2.

Detailed ways

Specific implementation method 1: Combined with Figures 1 to 6, this implementation method is described. A rotary direct-drive three-way pressure servo valve in this implementation method includes a main rotary valve subassembly 1, a valve core drive motor assembly 2 and a system sensing module 3. The main rotary valve subassembly 1 includes a valve sleeve 101, a valve core 102, a sealing cover 107, a valve body 109, a fixing flange 113, a sensor end cover 114 and a magnet fixing seat 110. The valve sleeve 101 is sleeved on the lower part of the valve core 102, and the sealing cover 107 The cover is arranged on the upper part of the valve core 102, the lower end of the sealing cover 107 is fixedly connected to the upper end of the valve sleeve 101, the valve body 109 is sleeved on the upper part of the valve sleeve 101, the lower end of the valve body 109 is connected to the upper end of the valve sleeve 101 through a thread, a sensor end cover 114 is arranged above the valve body 109, a fixing flange 113 is arranged between the sensor end cover 114 and the valve body 109, the sensor end cover 114, the fixing flange 113 and the valve body 109 are fixedly connected through a first connecting element 112, and the valve A magnet fixing seat 110 is installed at the upper end of the core 102, and the valve core drive motor assembly 2 includes a motor stator 201 and a motor rotor magnet 202. A motor rotor magnet 202 is provided between the valve core 102 and the sealing cover 107, and the motor stator 201 is sleeved on the upper end of the valve core 102. A motor stator 201 is provided between the sealing cover 107 and the valve body 109, and the motor stator 201 is sleeved in the middle of the sealing cover 107. The motor stator 201 and the motor rotor magnet 202 are correspondingly arranged; the system sensing module 3 includes a magnet 301, a magnetic angle sensor module 302 and a servo valve cable 303, the magnet 301 is installed on the magnet fixing seat 110, and a magnetic angle sensor module 302 is provided between the fixing flange 113 and the sensor end cover 114, the magnetic angle sensor module 302 and the fixing flange 113 are fixedly connected through the second connecting element 104, and one end of the servo valve cable 303 is connected to the magnetic angle sensor module 302.

In this embodiment, the middle of the valve core 102 is rotatably connected to the upper end of the valve sleeve 101 through the first bearing 105 ; the upper end of the valve core 102 is rotatably connected to the upper end of the sealing cover 107 through the second bearing 106 .

In this embodiment, a first sealing ring 103 is provided at the connection between the valve sleeve 101 and the sealing cover 107; among the valve sleeve 101, the valve core 102, and the sealing cover 107, only the first sealing ring 103 is used for static sealing between the valve sleeve 101 and the sealing cover 107, and there is no dynamic sealing, thereby reducing the radial friction force when the valve core 102 rotates.

In this embodiment, the first connecting element 112 is a first screw, the number of the first screws is three, and the fixing flange 113, the sensor end cover 114 and the valve body 109 are connected by the three first screws. Two second sealing rings 111 are respectively provided at the connection between the upper end of the fixing flange 113 and the lower end of the sensor end cover 114, and at the connection between the lower end of the fixing flange 113 and the upper end of the valve body 109. The fixing flange 113, the sensor end cover 114 and the valve body 109 are sealed by the two second sealing rings 111.

The fixing flange 113 also serves to limit the axial movement of the sealing cover 107 .

The valve body 109 is designed with threads on the outside, so that the rotary direct-drive servo valve can be connected to the hydraulic system through the threads of the valve body 109. The rotary direct-drive servo valve is fixedly installed with the equipment in a plug-in type.

In this embodiment, the second connecting element 104 is a second screw, the number of the second screws is two, and the magnetic angle sensor module 302 and the fixing flange 113 are connected by the two second screws.

In this embodiment, the motor stator 201 is mounted on the valve body 109 and fixed by the step structure of the valve body 109 and the fixing flange 113. The motor rotor magnet 202 is mounted on the valve core 102 and fixed by the step structure of the valve core 102. The motor rotor magnet 202 includes a hollow shaft and six magnet blocks evenly arranged along the circumferential direction. It is convenient for separate processing. Since the valve core 102 requires much higher processing accuracy and the valve core 102 is not magnetic, a hollow shaft is required to connect the rotor magnet and the valve core 102.

The motor stator 201 receives the motion information from the driver through the servo valve cable 303. The sensor module 302 determines the rotation angle of the valve core 102 by sensing the change of the magnetic flux of the magnet 301, and feeds back the information to the controller through the servo valve cable 303.

Specific implementation method 2: This implementation method is explained in conjunction with Figures 3 and 6. The main rotary valve subassembly 1 of this implementation method also includes two silicon steel sheets 108, which are respectively arranged on the upper and lower sides of the motor stator 201. The silicon steel sheets 108 are coaxially arranged with the motor stator 201. In this arrangement, the silicon steel sheets 108 are stacked together and wound with copper coils to form the stator of the motor. When the coil is energized, a magnetic field is generated in the silicon steel sheets 108, thereby driving the rotor to rotate. Other components and connection relationships are the same as those of the specific implementation method 1.

Specific embodiment three: This embodiment is described in conjunction with Figures 1 to 3, 5 and 6. The main rotary valve subassembly 1 of this embodiment further includes a wire ring 115. The upper end of the sensor end cover 114 is provided with an axially arranged wire ring assembly through hole. The wire ring 115 is installed in the wire ring assembly through hole. The other end of the servo valve cable 303 passes through the wire ring 115 and extends to the outside. The servo valve cable 303 is fixed to the sensor end cover 114 through the wire ring 115. Other components and connection relationships are the same as those of specific embodiments one or two.

Specific embodiment 4: This embodiment is described in conjunction with FIG. 3 and FIG. 6. The magnet fixing seat 110 of this embodiment is a columnar structure with a T-shaped cross section. The center of the upper end surface of the valve core 102 is provided with a fixing seat assembly countersunk hole along the axial direction. The lower end of the magnet fixing seat 110 is inserted into the fixing seat assembly countersunk hole. The center of the upper surface of the magnet fixing seat 110 is provided with a magnet assembly groove, and the magnet 301 is installed in the magnet assembly groove. Other components and connection relationships are the same as those of specific embodiments 1, 2 or 3.

Specific embodiment 5: This embodiment is explained in conjunction with Figures 3, 6 to 11. The valve core 102 and valve sleeve 101 of this embodiment divide the oil circuit into P oil chamber 402, T oil chamber 404, A oil chamber 403 and B oil chamber 401. When the motor stator 201 drives the valve core 102 to perform radial rotation in the valve sleeve 101, the throttle port and flow groove provided on the valve core 102 and the valve sleeve 101 can realize the connection and switching between the A oil chamber 403, the B oil chamber 401, the P oil chamber 402 and the T oil chamber 404, so that it has a three-position four-way function. Other components and connection relationships are the same as those of specific embodiments 1, 2, 3 or 4.

Specific embodiment six: This embodiment is described in conjunction with Figures 3, 6 to 11. The valve sleeve 101 of this embodiment is an annular structure, and four pairs of shaft shoulders are provided on the valve sleeve 101. The four pairs of shaft shoulders isolate three oil chambers from the valve sleeve 101, which are respectively B oil chamber 401, P oil chamber 402 and A oil chamber 403 from top to bottom. The P oil chamber 402 is connected to the oil outlet pipeline, and the A oil chamber 403 and the B oil chamber 401 are respectively connected to two oil circuits of the load;

The A oil chamber 403 of the valve sleeve 101 is provided with a first throttle port A1 and a second throttle port A2 arranged in a circumferentially symmetrical manner;

The oil chamber B 401 of the valve sleeve 101 is provided with a third throttle port B1 and a fourth throttle port B2 which are arranged symmetrically in a circumference;

The P oil chamber 402 of the valve sleeve 101 is provided with a first oil outlet P1 and a second oil outlet P2 arranged symmetrically in a circumference. Other components and connection relationships are the same as those of the first, second, third, fourth or fifth specific embodiments.

Specific embodiment seven: This embodiment is described in conjunction with FIG. 3 and FIG. 6 to FIG. 11 . The valve core 102 of this embodiment is a hollow structure, and a T oil chamber 404 is provided inside the valve core 102 . The T oil chamber 404 is connected to the oil return line;

The valve core 102 is provided with a first flow groove C1 and a second flow groove C2 arranged symmetrically in a circumference, and one end of the first flow groove C1 and the second flow groove C2 are connected to the P oil chamber 402 through the first oil outlet P1 and the second oil outlet P2 respectively;

The valve core 102 is provided with a fifth throttle port D1 and a sixth throttle port D2 arranged symmetrically in a circumference, and both the fifth throttle port D1 and the sixth throttle port D2 are communicated with the T oil chamber 404. Other components and connection relationships are the same as those of the first, second, third, fourth, fifth or sixth embodiments.

Specific implementation eight: This implementation is described in conjunction with Figures 3, 6 to 11. The valve core 102 of this implementation makes radial rotational motion in the valve sleeve 101. When the valve core 102 rotates a certain angle, the fifth throttle port D1 on the valve core 102 coincides with the third throttle port B1 of the B oil chamber 401 on the valve sleeve 101, so that the B oil chamber 401 communicates with the T oil chamber 404. At the same time, the other end of the first flow groove C1 on the valve core 102 coincides with the first throttle port A1 of the A oil chamber 403 on the valve sleeve 101, so that the A oil chamber 403 communicates with the P oil chamber 402. At this time, the load moves in one direction, and the speed of the movement is determined by the size of the position overlap.

The first flow groove C1 and the fifth throttle port D1 are aligned in the axial direction, and the first throttle port A1 and the third throttle port B1 are aligned in the axial direction, which can ensure that the oil outlet and the oil return paths have the same overlap at the throttle ports. Other components and connection relationships are the same as those of the specific embodiments one, two, three, four, five, six or seven.

Specific embodiment nine: This embodiment is described in conjunction with Figures 3, 6 to 11. The valve core 102 of this embodiment performs radial rotational motion in the valve sleeve 101. When the valve core 102 rotates a certain angle, the sixth throttle port D2 on the valve core 102 coincides with the first throttle port A1 of the A oil chamber 403 on the valve sleeve 101, so that the A oil chamber 403 communicates with the T oil chamber 404. At the same time, the other end of the second flow groove C2 on the valve core 102 coincides with the fourth throttle port B2 of the B oil chamber 401 on the valve sleeve 101, so that the B oil chamber 401 communicates with the P oil chamber 402. At this time, the load moves in the opposite direction, and the speed of the movement is determined by the size of the position overlap.

The second flow groove C2 and the sixth throttle port D2 are aligned in the axial direction, and the second throttle port A2 and the fourth throttle port B2 are aligned in the axial direction, which can ensure that the oil outlet and the oil return paths have the same overlap at the throttle port. Other components and connection relationships are the same as those of the first, second, third, fourth, fifth, sixth, seventh or eighth specific embodiments.

Specific embodiment ten: This embodiment is described in conjunction with Figures 3, 6 to 11. In this embodiment, the valve core 102 performs radial rotation in the valve sleeve 101. When the valve core 102 rotates a certain angle, the fifth throttle port D1 and the sixth throttle port D2 on the valve core 102 are not overlapped with the first throttle port A1 and the second throttle port A2 of the A oil chamber 403 on the valve sleeve 101 and the third throttle port B1 and the fourth throttle port B2 of the B oil chamber 401 on the valve sleeve 101. The A oil chamber 403, the B oil chamber 401 and the T oil chamber 404 are not connected, and the other ends of the first flow groove C1 and the second flow groove C2 on the valve core 102 do not overlap with the first throttle port A1 and the second throttle port A2 of the A oil chamber 403 on the valve sleeve 101 and the third throttle port B1 and the fourth throttle port B2 of the B oil chamber 401 on the valve sleeve 101, so that the A oil chamber 403, the B oil chamber 401 and the P oil chamber 402 are not connected, and the servo valve is in the middle position. The other components and connection relationships are the same as those of the first, second, third, fourth, fifth, sixth, seventh, eighth or ninth embodiment.

working principle

The working principle of a rotary direct-drive three-way pressure servo valve of the present invention is explained in conjunction with Figures 1 to 11: The present invention designs specific hydraulic windows at corresponding positions on the valve core and the valve sleeve to output the oil supply chamber pressure to the working chamber. When the motor driver supplies the driving current to the motor, the motor rotor part rotates to drive the valve core connected to the rotor to rotate. When the valve core and the valve sleeve rotate relative to each other, the window size changes, and the pressure difference at both ends of the window changes, thereby achieving pressure control. The present invention has a simple structure, is easy to process and assemble, has high control linearity, has a high success rate, and has high anti-pollution ability.

The above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit the same. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that the technical solutions described in the aforementioned embodiments may still be modified, or some of the technical features thereof may be replaced by equivalents. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims (10)

1. A rotatory tee bend pressure servo valve that directly drives, its characterized in that: the motor comprises a main rotary valve auxiliary assembly (1), a valve core driving motor assembly (2) and a system sensing module (3), wherein the main rotary valve auxiliary assembly (1) comprises a valve sleeve (101), a valve core (102), a sealing cover (107), a valve body (109), a fixing flange (113) and a sensor end cover (114) and a magnet fixing seat (110), the valve sleeve (101) is sleeved at the lower part of the valve core (102), the sealing cover (107) is covered at the upper part of the valve core (102), the lower end of the sealing cover (107) is fixedly connected with the upper end of the valve sleeve (101), the valve body (109) is sleeved at the upper part of the valve sleeve (101), the lower end of the valve body (109) is connected with the upper end of the valve sleeve (101) through threads, the sensor end cover (114) is arranged above the valve body (109), the fixing flange (113) is arranged between the sensor end cover (114) and the valve body (109), the fixing flange (113) and the valve body (109) are fixedly connected through a first connecting element (112), the magnet fixing seat (110) is arranged at the upper end of the valve core (102), the motor assembly (2) comprises a motor (202) and a magnet (201) between the motor and the rotor (102), the motor stator (201) is sleeved at the upper end of the valve core (102), a motor stator (201) is arranged between the sealing cover (107) and the valve body (109), the motor stator (201) is sleeved in the middle of the sealing cover (107), and the motor stator (201) and the motor rotor magnet (202) are correspondingly arranged; the system perception module (3) comprises a magnet (301), a magnetic angle sensor module (302) and a servo valve cable (303), wherein the magnet (301) is installed on a magnet fixing seat (110), the magnetic angle sensor module (302) is arranged between a fixing flange (113) and a sensor end cover (114), the magnetic angle sensor module (302) is fixedly connected with the fixing flange (113) through a second connecting element (104), and one end of the servo valve cable (303) is connected with the magnetic angle sensor module (302).

2. The rotary direct drive three-way pressure servo valve of claim 1, wherein: the main rotary valve auxiliary assembly (1) further comprises two silicon steel sheets (108), the two silicon steel sheets (108) are respectively arranged on the upper side and the lower side of the motor stator (201), and the silicon steel sheets (108) and the motor stator (201) are coaxially arranged.

3. A rotary direct drive three-way pressure servo valve according to claim 1 or 2, characterized in that: the main rotary valve auxiliary assembly (1) further comprises a wire passing ring (115), an axially arranged wire passing ring assembly through hole is formed in the upper end of the sensor end cover (114), the wire passing ring (115) is arranged in the wire passing ring assembly through hole, the other end of the servo valve cable (303) penetrates the wire passing ring (115) and extends to the outside, and the servo valve cable (303) is fixed on the sensor end cover (114) through the wire passing ring (115).

4. A rotary direct drive three-way pressure servo valve as claimed in claim 3, wherein: the magnet fixing seat (110) is of a columnar structure with a T-shaped section, a fixing seat assembly counter bore is formed in the center of the upper end face of the valve core (102) along the axial direction, the lower end of the magnet fixing seat (110) is inserted into the fixing seat assembly counter bore, a magnet assembly groove is formed in the center of the upper surface of the magnet fixing seat (110), and the magnet (301) is installed in the magnet assembly groove.

5. A rotary direct drive three-way pressure servo valve according to claim 1 or 4, wherein: the valve core (102) and the valve sleeve (101) divide an oil path into a P oil chamber (402), a T oil chamber (404), an A oil chamber (403) and a B oil chamber (401), and when the motor stator (201) drives the valve core (102) to do radial rotation movement in the valve sleeve (101), the on-off and reversing between the A oil chamber (403), the B oil chamber (401), the P oil chamber (402) and the T oil chamber (404) can be realized through a throttle opening and a circulating groove formed in the valve core (102) and the valve sleeve (101), so that the motor stator (201) has a three-position four-way function.

6. The rotary direct drive three-way pressure servo valve of claim 5, wherein: the valve sleeve (101) is of an annular structure, four pairs of shaft shoulders are arranged on the valve sleeve (101), the four pairs of shaft shoulders isolate the valve sleeve (101) into three oil chambers, namely a B oil chamber (401), a P oil chamber (402) and an A oil chamber (403) from top to bottom, the P oil chamber (402) is communicated with an oil outlet pipeline, and the A oil chamber (403) and the B oil chamber (401) are respectively communicated with two oil paths of a load;

wherein, the A oil cavity (403) of the valve sleeve (101) is provided with a first throttling opening (A1) and a second throttling opening (A2) which are symmetrically arranged according to the circumference;

Wherein, a third choke (B1) and a fourth choke (B2) which are symmetrically arranged according to the circumference are arranged on the B oil cavity (401) of the valve sleeve (101);

The P oil cavity (402) of the valve sleeve (101) is provided with a first oil outlet (P1) and a second oil outlet (P2) which are symmetrically arranged according to the circumference.

7. The rotary direct drive three-way pressure servo valve of claim 6, wherein: the valve core (102) is of a hollow structure, a T oil cavity (404) is arranged in the valve core (102), and the T oil cavity (404) is communicated with an oil return pipeline;

the valve core (102) is provided with a first circulation groove (C1) and a second circulation groove (C2) which are symmetrically arranged according to the circumference, and one ends of the first circulation groove (C1) and the second circulation groove (C2) are respectively communicated with the P oil cavity (402) through a first oil outlet (P1) and a second oil outlet (P2);

the valve core (102) is provided with a fifth throttle orifice (D1) and a sixth throttle orifice (D2) which are symmetrically arranged according to the circumference, and the fifth throttle orifice (D1) and the sixth throttle orifice (D2) are communicated with the T oil cavity (404).

8. The rotary direct drive three-way pressure servo valve of claim 7, wherein: the valve core (102) radially rotates in the valve sleeve (101), after the valve core (102) rotates for a certain angle, a fifth throttle orifice (D1) on the valve core (102) is overlapped with a third throttle orifice (B1) of a B oil cavity (401) on the valve sleeve (101) to enable the B oil cavity (401) to be communicated with a T oil cavity (404), meanwhile, the other end of a first circulation groove (C1) on the valve core (102) is overlapped with a first throttle orifice (A1) of an A oil cavity (403) on the valve sleeve (101) to enable the A oil cavity (403) to be communicated with a P oil cavity (402), at the moment, a load moves towards one direction, and the movement speed is determined by the degree of position overlap ratio;

The first throttling port (A1) and the third throttling port (B1) are aligned in the axial direction, and the coincidence degree of the oil outlet and the oil return at the time at the throttling port can be guaranteed to be consistent.

9. The rotary direct drive three-way pressure servo valve of claim 8, wherein: the valve core (102) radially rotates in the valve sleeve (101), after the valve core (102) rotates for a certain angle, a sixth throttle orifice (D2) on the valve core (102) is overlapped with a first throttle orifice (A1) of an A oil cavity (403) on the valve sleeve (101) to enable the A oil cavity (403) to be communicated with a T oil cavity (404), meanwhile, the other end of a second flow groove (C2) on the valve core (102) is overlapped with a fourth throttle orifice (B2) of a B oil cavity (401) on the valve sleeve (101) to enable the B oil cavity (401) to be communicated with a P oil cavity (402), at the moment, a load moves in the opposite direction, and the movement speed is determined by the degree of position overlap;

The second flow groove (C2) and the sixth throttling port (D2) are aligned in the axial direction, the second throttling port (A2) and the fourth throttling port (B2) are aligned in the axial direction, and the coincidence degree of the oil outlet and the oil return passage at the moment at the throttling port can be guaranteed to be consistent.

10. The rotary direct drive three-way pressure servo valve of claim 9, wherein: the valve core (102) radially rotates in the valve sleeve (101), after the valve core (102) rotates for a certain angle, the fifth throttle orifice (D1) and the sixth throttle orifice (D2) on the valve core (102) are not overlapped with the first throttle orifice (A1), the second throttle orifice (A2) of the A oil cavity (403) on the valve sleeve (101) and the third throttle orifice (B1) and the fourth throttle orifice (B2) of the B oil cavity (401) on the valve sleeve (101), so that the A oil cavity (403), the B oil cavity (401) are not communicated with the T oil cavity (404), and meanwhile, the other end of the first circulation groove (C1) and the second circulation groove (C2) on the valve core (102) are not overlapped with the first throttle orifice (A1) and the second throttle orifice (A2) of the A oil cavity (403) on the valve sleeve (101) and the third throttle orifice (B1) and the fourth throttle orifice (B2) of the B oil cavity (401) on the valve sleeve (101), so that the A oil cavity (403), the B oil cavity (401) and the P oil cavity (402) are not communicated with each other, and the servo valve is in a neutral position.