CN118361425A - Rotatory tee bend pressure servo valve that directly drives - Google Patents
Rotatory tee bend pressure servo valve that directly drives Download PDFInfo
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- CN118361425A CN118361425A CN202410654282.0A CN202410654282A CN118361425A CN 118361425 A CN118361425 A CN 118361425A CN 202410654282 A CN202410654282 A CN 202410654282A CN 118361425 A CN118361425 A CN 118361425A
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- 238000007789 sealing Methods 0.000 claims abstract description 27
- 239000003921 oil Substances 0.000 claims description 178
- 229910000976 Electrical steel Inorganic materials 0.000 claims description 12
- 230000006870 function Effects 0.000 claims description 4
- 230000007935 neutral effect Effects 0.000 claims description 4
- 230000008447 perception Effects 0.000 claims description 4
- 238000012423 maintenance Methods 0.000 abstract description 3
- 239000000203 mixture Substances 0.000 description 9
- 238000010586 diagram Methods 0.000 description 3
- 238000003754 machining Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
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- 230000004907 flux Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
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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
Technical Field
The invention relates to the technical field of electrohydraulic servo valves, in particular to a rotary direct-drive three-way pressure servo valve.
Background
The pressure servo valve is used as a key element in a hydraulic control system, is a hydraulic control valve for converting an electric signal into output pressure of a load port, has the advantages of small leakage, quick response, high control precision and the like, and is widely applied to the fields of brake systems, robots and the like. However, the traditional pressure servo valve adopts a nozzle baffle plate type and a jet pipe type as a servo valve pilot stage, adopts pressure negative feedback to realize pressure regulation, has the defects of large volume, complex structure, large internal leakage, high processing and maintenance cost and the like, and limits the application of the pressure servo valve in the scenes of high energy efficiency and high frequency response.
Disclosure of Invention
The invention aims to solve 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 technical scheme of the invention is as follows:
The rotary direct-drive three-way pressure servo valve 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 fixed 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, the sealing cover 107 is covered on 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 on 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 fixed flange 113 is arranged between the sensor end cover 114 and the valve body 109, the fixed flange 113 is fixedly connected with the valve body 109 through a first connecting element 112, the upper end of the valve core 102 is provided with a magnet fixing seat 110, the valve core driving motor assembly 2 comprises a motor stator 201 and a motor rotor magnet 202, the valve core 102 and the sealing cover 107 are arranged 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, the motor stator 201 is arranged between the sealing cover 107 and the motor stator 201 is sleeved on the middle part of the sealing cover 201 and the motor stator 201 is correspondingly arranged between the motor stator 201 and the valve body 201; 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 the magnet fixing seat 110, the magnetic angle sensor module 302 is arranged 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 with the magnetic angle sensor module 302.
Further, 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 are coaxially arranged with the motor stator 201.
Further, the main rotary valve sub-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 installed in the wire passing ring assembly through hole, the other end of the servo valve cable 303 passes through 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.
Further, the magnet fixing seat 110 has a columnar structure with a T-shaped section, the center of the upper end surface of the valve core 102 is provided with a fixing seat assembly counter bore along the axial direction, the lower end of the magnet fixing seat 110 is inserted into the fixing seat assembly counter bore, 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.
Further, 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 among 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 the throttle opening and the flow groove arranged on the valve core 102 and the valve sleeve 101, so that the three-position four-way function is realized.
Further, 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 an oil chamber B401, an oil chamber P402 and an oil chamber A403 from top to bottom, the oil chamber P402 is communicated with an oil outlet pipeline, and the oil chamber A403 and the oil chamber B401 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 throttle opening A1 and a second throttle opening A2 which are symmetrically arranged according to the circumference;
Wherein, the third throttle port B1 and the fourth throttle port B2 which are symmetrically arranged according to the circumference are arranged on the B oil cavity 401 of the valve sleeve 101;
the first oil outlet P1 and the second oil outlet P2 are symmetrically arranged according to the circumference and are arranged on the P oil cavity 402 of the valve sleeve 101.
Further, the valve core 102 is of a hollow structure, a T-shaped oil cavity 404 is arranged in the valve core 102, and the T-shaped oil cavity 404 is communicated with an oil return pipeline;
The spool 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 choke D1 and a sixth choke D2 which are symmetrically arranged according to the circumference, and the fifth choke D1 and the sixth choke D2 are both communicated with the T oil cavity 404.
Further, the valve core 102 performs radial rotation movement in the valve sleeve 101, after the valve core 102 rotates for a certain angle, the fifth throttle orifice D1 on the valve core 102 coincides with the third throttle orifice B1 of the B oil cavity 401 on the valve sleeve 101, so that the B oil cavity 401 is communicated with the T oil cavity 404, meanwhile, the other end of the first flow groove C1 on the valve core 102 coincides with the first throttle orifice A1 of the A oil cavity 403 on the valve sleeve 101, so that the A oil cavity 403 is communicated with the P oil cavity 402, at the moment, the load moves towards one direction, and the movement speed is determined by the degree of position coincidence;
the first throttling port A1 and the third throttling port B1 are aligned in the axial direction, so that the coincidence degree of the oil outlet and the oil return at the moment at the throttling port can be ensured to be consistent.
Further, the valve core 102 performs radial rotation movement in the valve sleeve 101, after the valve core 102 rotates for a certain angle, a sixth throttle D2 on the valve core 102 coincides with a first throttle A1 of an a oil cavity 403 on the valve sleeve 101, so that the a oil cavity 403 is communicated with a T oil cavity 404, and meanwhile, the other end of a second flow groove C2 on the valve core 102 coincides with a fourth throttle B2 of a B oil cavity 401 on the valve sleeve 101, so that the B oil cavity 401 is communicated with the 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 coincidence;
The second flow groove C2 and the sixth orifice D2 are aligned in the axial direction, and the second orifice A2 and the fourth orifice B2 are aligned in the axial direction, so that the coincidence ratio of the oil outlet and the oil return at the moment at the orifice can be ensured to be consistent.
Further, the valve core 102 performs radial rotation movement in the valve housing 101, after the valve core 102 rotates by 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 and the second throttle orifice A2 of the a oil cavity 403 on the valve housing 101 and the third throttle orifice B1 and the fourth throttle orifice B2 of the B oil cavity 401 on the valve housing 101, so that the a oil cavity 403 and the B oil cavity 401 are not communicated with the T oil cavity 404, and meanwhile, the other ends of the first flow groove C1 and the second flow 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 housing 101 and the third throttle orifice B1 and the fourth throttle orifice B2 of the B oil cavity 401 on the valve housing 101, so that the a oil cavity 403 and the B oil cavity 401 are not communicated with the P oil cavity 402, and the servo valve is in the neutral position.
Compared with the prior art, the invention has the following effects:
1. the invention adopts the structure design of the screw-in cartridge valve, has fewer valve body component parts, integrally designs the motor rotor and the valve core, and has the advantages of small volume, compact structure, simple assembly, high integration degree and the like.
2. According to the invention, the valve core, the valve sleeve and the valve body can be sealed by adopting the first sealing ring, dynamic sealing is avoided, leakage is avoided, radial friction force of the valve core during rotation is greatly reduced, and energy efficiency of the servo valve is improved.
3. According to the invention, a rotary valve core design is adopted, the valve core is driven by a motor rotor to rotate relative to the valve sleeve, so that the on-off and reversing between the load cavity and the P oil cavity and between the load cavity and the T oil cavity are realized, the three-position two-way function is realized, the overlap ratio of the valve core and the throttling port on the valve sleeve is controlled by controlling the valve core rotation angle, the accurate control of the pressure is realized, and the pressure control precision of the servo valve is improved.
4. The invention designs the throttle opening and the oil outlet which are symmetrically arranged according to the circumference on the valve sleeve, designs the throttle opening and the flow groove which are symmetrically arranged according to the circumference on the valve core, and the throttle opening and the flow groove are orderly aligned in the axial direction, thereby realizing hydraulic balance when the valve core rotates and reducing the rotating resistance of the motor rotor.
Drawings
FIG. 1 is an isometric view of a rotary direct drive three-way pressure servo valve of the present invention;
FIG. 2 is a general assembly view of a rotary direct drive three-way pressure servo valve of the present invention;
FIG. 3 is a general assembly view of a valve body assembly of a rotary direct drive three-way pressure servo valve of the present invention;
FIG. 4 is a general assembly view of a motor assembly of a rotary direct drive three-way pressure servo valve of the present invention;
FIG. 5 is a general assembly diagram of a system sensing module of a rotary direct-drive three-way pressure servo valve of the present invention;
FIG. 6 is a schematic diagram of a rotary direct-drive three-way pressure servo valve according to the present invention;
FIG. 7 is an expanded view of a valve housing cylinder section structure of a rotary direct drive three-way pressure servo valve of the present invention;
FIG. 8 is an expanded view of the cylindrical portion structure of the spool of a rotary direct-drive three-way pressure servo valve of the present invention;
FIG. 9 is a schematic illustration of a rotary direct drive three-way pressure servo valve of the present invention in a first operating condition;
FIG. 10 is a schematic illustration of a rotary direct drive three-way pressure servo valve of the present invention in a second operational state;
Fig. 11 is a schematic diagram of a rotary direct drive three-way pressure servo valve of the present invention in a neutral state.
In the figure: 1 is a main rotary valve auxiliary component; 2 is a valve core driving motor component; 3 is a system perception module; 101 is a valve sleeve; 102 is a valve core; 103 is a first seal ring; 104 is a second connecting element; 105 is a first bearing; 106 is a second bearing; 107 is a sealing cover; 108 is a silicon steel sheet; 109 is the valve body; 110 is a magnet holder; 111 is a second seal ring; 112 is a first connecting element; 113 is a fixed flange; 114 is a sensor end cap; 115 is a wire loop; 201 is a motor stator; 202 is a motor rotor magnet; 301 is a magnet; 302 is a magnetic angle sensor module; 303 is a servo valve cable; b oil chamber 401; p oil chamber 402; an oil chamber 403; a T oil chamber 404; a first orifice A1; a second orifice A2; a third orifice B1; a fourth orifice B2; a first oil outlet P1; a second oil outlet P2; a first flow channel C1; a second flow-through tank C2; a fifth orifice D1; and a sixth orifice D2.
Detailed Description
The first embodiment is as follows: referring to fig. 1 to 6, a rotary direct-drive three-way pressure servo valve of the present embodiment is described, which includes a main rotary valve sub-assembly 1, a valve core driving motor assembly 2 and a system sensing module 3, the main rotary valve sub-assembly 1 includes a valve housing 101, a valve core 102, a seal cover 107, a valve body 109, a fixing flange 113, a sensor end cap 114 and a magnet fixing seat 110, the valve housing 101 is sleeved at the lower part of the valve core 102, the seal cover 107 is covered at the upper part of the valve core 102, the lower end of the seal cover 107 is fixedly connected with the upper end of the valve housing 101, the valve body 109 is sleeved at the upper part of the valve housing 101, the lower end of the valve body 109 is connected with the upper end of the valve housing 101 through threads, the sensor end cap 114 is arranged above the valve body 109, the fixing flange 113 is arranged between the sensor end cap 114 and the valve body 109, the fixing flange 113 is fixedly connected with the valve body 109 through a first connecting element 112, the upper end of the valve core 102 is provided with a magnet fixing seat 110, the valve core driving motor assembly 2 includes a motor stator 201 and a motor rotor magnet 202, a motor rotor magnet 202 is arranged between the valve core 102 and the seal cover 107, the motor stator 201 is sleeved at the upper end of the motor stator 201 and the motor stator 201 is correspondingly arranged between the motor stator 201 and the valve body 107; 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 the magnet fixing seat 110, the magnetic angle sensor module 302 is arranged 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 with the magnetic angle sensor module 302.
In the embodiment, the middle part of the valve core 102 is rotationally connected with the upper end of the valve sleeve 101 through a first bearing 105; the upper end of the valve core 102 is rotatably connected with the upper end of the sealing cover 107 through a second bearing 106.
In the present embodiment, a first seal ring 103 is provided at the junction of the valve housing 101 and the seal cover 107; the valve sleeve 101, the valve core 102 and the sealing cover 107 are in static sealing by the first sealing ring 103, and dynamic sealing is omitted, so that radial friction force of the valve core 102 during rotation is reduced.
In this embodiment, the first connecting elements 112 are first screws, the number of the first screws is three, and the fixing flange 113, the sensor end cap 114 and the valve body 109 are connected by three first screws. Two second sealing rings 111 are respectively arranged at the connection part of the upper end of the fixed flange 113 and the lower end of the sensor end cover 114 and the connection part of the lower end of the fixed flange 113 and the upper end of the valve body 109. The fixing flange 113, the sensor end cap 114 and the valve body 109 are sealed by two second sealing rings 111.
The fixing flange 113 also serves, among other things, to limit the axial movement of the sealing cap 107.
The screw thread is designed outside the valve body 109, so that the rotary direct-drive servo valve can be connected with a hydraulic system through the screw thread of the valve body 109. The rotary direct-drive servo valve is fixedly installed with equipment by adopting plug-in mounting.
In this embodiment, the second connection elements 104 are second screws, the number of the second screws is two, and the magnetic angle sensor module 302 and the fixing flange 113 are connected by two second screws.
In the present embodiment, the motor stator 201 is mounted on the valve body 109 and is fixed by the stepped structure of the valve body 109 and the fixing flange 113. The motor rotor magnet 202 is mounted on the valve core 102 and is fixed by the stepped structure of the valve core 102. The motor rotor magnet 202 includes a hollow shaft and six magnet pieces uniformly arranged in the circumferential direction. The split machining is facilitated, and since the spool 102 requires much higher machining accuracy, the spool 102 is magnetically non-conductive, and therefore a hollow shaft is required to connect the rotor magnet and the spool 102.
Wherein, the motor stator 201 receives the action information sent by the driver through the servo valve cable 303. The sensor module 302 determines the rotation angle of the valve core 102 by sensing the magnetic flux change of the magnet 301, and feeds information back to the controller through the servo valve cable 303.
The second embodiment is as follows: the main rotary valve sub-assembly 1 of the present embodiment further includes two silicon steel sheets 108, the two silicon steel sheets 108 being disposed on the upper and lower sides of the motor stator 201, respectively, the silicon steel sheets 108 being disposed coaxially with the motor stator 201, as described with reference to fig. 3 and 6. The arrangement is that the silicon steel sheets 108 are overlapped together, a copper coil is wound to form a stator of the motor, and a magnetic field is generated in the silicon steel sheets 108 after the coil is electrified, so that the rotor is driven to rotate. Other compositions and connection relationships are the same as those of the first embodiment.
And a third specific embodiment: the main rotary valve sub-assembly 1 of the present embodiment further includes a wire ring 115, an axially arranged wire ring assembly through hole is provided at the upper end of the sensor end cap 114, 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, and the servo valve cable 303 is fixed on the sensor end cap 114 through the wire ring 115. Other compositions and connection relationships are the same as those of the first or second embodiment.
The specific embodiment IV is as follows: referring to fig. 3 and 6, the magnet fixing seat 110 of the present embodiment has 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 counterbore along the axial direction, the lower end of the magnet fixing seat 110 is inserted into the fixing seat assembly counterbore, 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 compositions and connection relationships are the same as those of the first, second or third embodiments.
Fifth embodiment: in the present embodiment, the valve core 102 and the valve housing 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 perform radial rotation movement in the valve housing 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 the chokes and the flow grooves formed in the valve core 102 and the valve housing 101, so that the three-position four-way function is provided. Other compositions and connection relationships are the same as those of the first, second, third or fourth embodiments.
Specific embodiment six: the valve sleeve 101 of the present embodiment is in an annular structure, and four pairs of shaft shoulders are arranged on the valve sleeve 101, and isolate the valve sleeve 101 into three oil chambers, namely, an oil chamber B401, an oil chamber P402 and an oil chamber A403 from top to bottom, wherein the oil chamber P402 is communicated with an oil outlet pipeline, and the oil chamber A403 and the oil chamber B401 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 throttle opening A1 and a second throttle opening A2 which are symmetrically arranged according to the circumference;
Wherein, the third throttle port B1 and the fourth throttle port B2 which are symmetrically arranged according to the circumference are arranged on the B oil cavity 401 of the valve sleeve 101;
The first oil outlet P1 and the second oil outlet P2 are symmetrically arranged according to the circumference and are arranged on the P oil cavity 402 of the valve sleeve 101. Other compositions and connection relationships are the same as those of the first, second, third, fourth or fifth embodiments.
Seventh embodiment: referring to fig. 3 and fig. 6 to fig. 11, the valve core 102 of the present embodiment is of a hollow structure, and a T oil cavity 404 is disposed in the valve core 102, and the T oil cavity 404 is communicated with an oil return pipeline;
The spool 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 choke D1 and a sixth choke D2 which are symmetrically arranged according to the circumference, and the fifth choke D1 and the sixth choke D2 are both communicated with the T oil cavity 404. Other compositions and connection relationships are the same as those of the first, second, third, fourth, fifth or sixth embodiments.
Eighth embodiment: referring to fig. 3 and fig. 6 to fig. 11, in this embodiment, the valve core 102 performs radial rotation movement in the valve sleeve 101, after the valve core 102 rotates by a certain angle, the fifth throttle D1 on the valve core 102 coincides with the third throttle B1 of the B oil cavity 401 on the valve sleeve 101, so that the B oil cavity 401 is communicated with the T oil cavity 404, meanwhile, the other end of the first flow channel C1 on the valve core 102 coincides with the first throttle A1 of the a oil cavity 403 on the valve sleeve 101, so that the a oil cavity 403 is communicated with the P oil cavity 402, and at this time, the load moves in one direction, and the movement speed is determined by the degree of the position coincidence;
the first throttling port A1 and the third throttling port B1 are aligned in the axial direction, so that the coincidence degree of the oil outlet and the oil return at the moment at the throttling port can be ensured to be consistent. Other compositions and connection relationships are the same as those of the first, second, third, fourth, fifth, sixth or seventh embodiments.
Detailed description nine: referring to fig. 3 and fig. 6 to fig. 11, in this embodiment, the valve core 102 performs radial rotation movement in the valve sleeve 101, after the valve core 102 rotates by a certain angle, the sixth orifice D2 on the valve core 102 coincides with the first orifice A1 of the a oil cavity 403 on the valve sleeve 101, so that the a oil cavity 403 is communicated with the T oil cavity 404, meanwhile, the other end of the second flow channel C2 on the valve core 102 coincides with the fourth orifice B2 of the B oil cavity 401 on the valve sleeve 101, so that the B oil cavity 401 is communicated with the P oil cavity 402, and at this time, the load moves in the opposite direction, and the movement speed is determined by the degree of the position coincidence;
the second flow groove C2 and the sixth orifice D2 are aligned in the axial direction, and the second orifice A2 and the fourth orifice B2 are aligned in the axial direction, so that the coincidence ratio of the oil outlet and the oil return at the moment at the orifice can be ensured to be consistent. Other compositions and connection relationships are the same as those of the first, second, third, fourth, fifth, sixth, seventh or eighth embodiments.
Detailed description ten: in this embodiment, referring to fig. 3 and fig. 6 to fig. 11, the valve core 102 performs radial rotation movement in the valve housing 101, after the valve core 102 rotates by a certain angle, the fifth orifice D1 and the sixth orifice D2 on the valve core 102 are not overlapped with the first orifice A1 and the second orifice A2 of the a oil cavity 403 on the valve housing 101 and the third orifice B1 and the fourth orifice B2 of the B oil cavity 401 on the valve housing 101, so that the a oil cavity 403 and the B oil cavity 401 are not communicated with the T oil cavity 404, and meanwhile, the other ends of the first circulation groove C1 and the second circulation groove C2 on the valve core 102 are not overlapped with the first orifice A1 and the second orifice A2 of the a oil cavity 403 on the valve housing 101 and the third orifice B1 and the fourth orifice B2 of the B oil cavity 401 on the valve housing 101, so that the a oil cavity 403 and the B oil cavity 401 are not communicated with the P oil cavity 402, and the servo valve is in the neutral position. Other compositions and connection relationships are the same as those of the one, two, three, four, five, six, seven, eight or nine embodiments.
Principle of operation
The working principle of the rotary direct-drive three-way pressure servo valve of the invention is described with reference to fig. 1 to 11: the invention designs a specific hydraulic window at the corresponding position on the valve core and the valve sleeve, and outputs the pressure of the oil supply cavity to the working cavity. When the motor driver supplies driving current to the motor, the rotor part of the motor rotates to drive the valve core fixedly connected with the rotor to rotate, when the valve core rotates relative to the valve sleeve, the size of the window changes, and the pressure difference at the two ends of the window changes, so that pressure control is realized. The invention has simple structure, easy processing and assembly, high control linearity, higher success and high pollution resistance.
The above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410654282.0A CN118361425A (en) | 2024-05-24 | 2024-05-24 | Rotatory tee bend pressure servo valve that directly drives |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410654282.0A CN118361425A (en) | 2024-05-24 | 2024-05-24 | Rotatory tee bend pressure servo valve that directly drives |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN118361425A true CN118361425A (en) | 2024-07-19 |
Family
ID=91887121
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410654282.0A Pending CN118361425A (en) | 2024-05-24 | 2024-05-24 | Rotatory tee bend pressure servo valve that directly drives |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN118361425A (en) |
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2024
- 2024-05-24 CN CN202410654282.0A patent/CN118361425A/en active Pending
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