CN117738952A - Spiral positioning guide control type electrohydraulic proportional servo valve of valve sleeve - Google Patents

Abstract

The invention provides a valve-breaking sleeve spiral positioning guide control type electro-hydraulic proportional servo valve, which comprises a slide valve component, an oil port changing plate at the left end of the slide valve component and an electric actuator at the right end of the slide valve component, wherein the oil port changing plate is arranged at the left end of the slide valve component; a spool which is slidably provided in the axial direction inside the spool assembly, and a spool portion is inserted into the electric actuator; the electric actuator is internally and rotatably connected with a pilot stage valve sleeve, and the pilot stage valve sleeve is connected with a valve core insertion part; and a guide and control structure is arranged between the valve core insertion part and the guide and control stage valve sleeve. The invention successfully reduces the moment of inertia, so that the motor can drive the valve core to move with lower torque output; furthermore, the invention can also reduce the subsequent maintenance cost of the servo valve.

Description

Spiral positioning guide control type electrohydraulic proportional servo valve of valve sleeve

Technical Field

The invention relates to the technical field of proportional servo valves, in particular to a valve-breaking sleeve spiral positioning guide control type electro-hydraulic proportional servo valve.

Background

The proportional servo valve is a precise control element widely applied to the modern industry and the military field. And is also a core element of an electrohydraulic servo system. The hydraulic control system receives the electric signals and converts the electric signals into corresponding hydraulic signals, so that accurate control of the fluid power system is realized.

The Chinese patent application publication No. CN115823050A discloses a single-spring axial reset type two-dimensional motor direct-drive half-bridge two-dimensional electro-hydraulic servo valve, wherein the middle part of a motor outer rotor of the two-dimensional electro-hydraulic servo valve is in interference fit on the outer peripheral surface of the right end of a valve core. The valve core is directly driven to rotate by the outer rotor motor, and the pressure in the sensitive cavity of the valve body can be changed after the valve core rotates, so that the valve core is driven to axially move. For another example, the under-constrained outer rotor motor with the application publication number of CN115949638A directly drives a two-dimensional electrohydraulic servo valve, the double-spring axial reset type two-dimensional motor with the application publication number of CN115875499A directly drives a half-bridge two-dimensional electrohydraulic servo valve and the like. Said invented patent adopts the form of external rotor motor directly driving valve core to make it rotate by means of external rotor, but has the following defects: 1. the outer rotor directly drives the valve core to cause large moment of inertia, and the requirements on the motor are high during starting and reversing. 2. Further, because the outer rotor of the motor is directly connected with the outer peripheral surface of the right end of the valve core, the force arm is short, and therefore the motor is required to output larger torque to drive the valve core to rotate. 3. Furthermore, the two-dimensional servo valve spool in the prior art generally moves in two degrees of freedom of rotation and axial direction, and axial abrasion can be generated when the spool moves without decoupling. However, the decoupling mechanism is generally complex, and if there are too many parts, the processing cost is increased, and the subsequent repair and maintenance are more complicated. 4. The maintenance difficulty is high, because the outer rotor motor directly drives the valve core to rotate, if a servo screw mechanism on the valve core has a problem, the whole servo valve needs to be disassembled for maintenance.

Disclosure of Invention

Aiming at the defects existing in the prior art, the invention aims to provide the valve-breaking sleeve spiral positioning guide control type electro-hydraulic proportional servo valve. The invention successfully reduces the moment of inertia, so that the electric actuator can drive the valve core to move with lower torque output; furthermore, the invention can also reduce the subsequent maintenance cost of the servo valve.

In order to solve the technical problems, the invention is realized by the following technical scheme:

a valve-breaking sleeve spiral positioning guide control type electrohydraulic proportional servo valve is characterized in that: the electro-hydraulic proportional servo valve comprises a slide valve component, an oil port changing plate at the left end of the slide valve component and an electric actuator at the right end of the slide valve component; a spool which is slidably provided in the axial direction inside the spool assembly, and a spool portion is inserted into the electric actuator; the electric actuator is internally and rotatably connected with a pilot stage valve sleeve, and the pilot stage valve sleeve is connected with a valve core insertion part; and a guide and control structure is arranged between the valve core insertion part and the guide and control stage valve sleeve.

Further: the slide valve assembly comprises a valve body, a main valve sleeve coaxially arranged in the valve body and a valve core coaxially arranged in the main valve sleeve; the left end of the valve body is fixedly connected with the oil port changing plate, and the right end of the valve body is fixedly connected with the electric actuator.

Further: the electric actuator comprises a stator assembly, an outer rotor and a motor cover cylinder which are coaxially sleeved on the outer side of the pilot control stage valve sleeve in sequence, wherein the motor cover cylinder is fixedly connected with the slide valve assembly, a connecting plate is clamped between the motor cover cylinder and the slide valve assembly, the stator assembly is fixed on the connecting plate, and the outer rotor is fixedly connected with the pilot control stage valve sleeve.

Further: the outer rotor consists of a rotary sleeve and a magnetic steel assembly attached to the rotary sleeve, the rotary sleeve is provided with an annular side wall and an annular base which are integrally formed, and the annular base is fixedly connected with the right end of the pilot stage valve sleeve.

Further: the electric actuator is provided with an axial force bearing assembly, the axial force bearing assembly comprises a first thrust bearing and a second thrust bearing, and the pilot stage valve is sleeved between the first thrust bearing and the second thrust bearing.

Further: the valve core inserting part is provided with a high-pressure hole and a low-pressure hole, the guide and control stage valve sleeve is provided with a sensitive cavity channel matched with the high-pressure hole and the low-pressure hole, and the sensitive cavity channel is matched with the high-pressure hole and the low-pressure hole to form the guide and control structure.

Further: and a sealing plate is arranged in the guide and control valve sleeve, the sealing plate is arranged on the right side of the sensitive cavity channel, and the sealing plate and the right end face of the valve core form a sensitive cavity which is only communicated with the sensitive cavity channel.

Further: the slide valve assembly comprises a sealing ring coaxially sleeved on the outer side of the valve core and embedded in the main valve sleeve, a shoulder is arranged at the left end of the valve core, the shoulder, the main valve sleeve and the sealing ring form a high-pressure cavity communicated with a high-pressure flow passage of the slide valve assembly, and the high-pressure cavity is communicated with the high-pressure flow passage of the slide valve assembly.

Further: the slide valve assembly comprises a T-shaped plugging piece which is abutted against the left end of the main valve sleeve and is embedded in the valve body, a small head end of the T-shaped plugging piece extends into the main valve sleeve, an assembly groove matched with the valve core is formed in the end part of the small head end, and a travel distance for the valve core to axially move is formed between the valve core and the groove bottom of the assembly groove.

Further: the assembly groove is internally and fixedly provided with a rotary limiting piece which is in sliding connection with the valve core.

Compared with the prior art, the invention has the following advantages:

1. in the prior art, as the motor drives the valve core to rotate through the transmission mechanism, if the servo valve has a problem in working, the whole valve body may need to be disassembled for maintenance. In contrast, the outer rotor of the invention directly drives the pilot stage valve sleeve to rotate, the structure is relatively simple, the maintenance is more convenient, and only the unilateral motor is required to be disassembled.

2. The invention greatly reduces the mechanical friction existing in the working process of the decoupling mechanism, and effectively eliminates the adverse effect of nonlinear factors such as friction force and the like on the static characteristic of the electrohydraulic proportional servo valve; and also reduces the subsequent maintenance costs of the servo valve.

3. The invention takes the guide and control structure as a guide stage, namely a variable throttling orifice is formed between the sensitive cavity channel and the high-pressure hole and the low-pressure hole respectively, the high-pressure hole and the low-pressure hole are communicated with the sensitive cavity through the sensitive cavity channel, and the pressure of the sensitive cavity is equal to that of the high-pressure cavity. The invention has the advantages of good performance, high repeatability, linearity, response time and other performance indexes, simple structure, high flow, strong pollution resistance, high frequency response and the like compared with the products of the same type at home and abroad.

Drawings

FIG. 1 is a schematic view of the external structure of the present invention;

FIG. 2 is a schematic cross-sectional view of an exemplary embodiment of the present invention;

FIG. 3 is a schematic cross-sectional view of an electric actuator of the present invention;

FIG. 4 is a schematic structural view of the stator assembly of the present invention;

FIG. 5 is a schematic view of the structure of the valve cartridge of the present invention;

FIG. 6 is a schematic view of the structure of the connection plate of the present invention;

FIG. 7 is a schematic view of the structure of the rotating sleeve of the present invention;

FIG. 8 is a schematic structural view of a pilot stage valve sleeve of the present invention;

fig. 9 is a schematic structural view of the T-shaped stopper of the present invention.

Reference numerals: 1-a spool valve assembly; 2-oil port changing plate; 3-an electric actuator; 4-valve core; 5-guiding and controlling the valve sleeve; 6-rib plates; 7-a spool insertion portion; 8-a valve body; 9-a main valve sleeve; 10-a stator assembly; 11-an internal flow channel; 12-a motor cover cylinder; 13-rotating the sleeve; 14-magnetic steel components; 15-annular side walls; 16-an annular base; 17-a first thrust bearing; 18-a second thrust bearing; 19-high pressure holes; 20-low pressure holes; 21-sensitive cavity channel; 22-closing plate; 23-sensitive cavity; 24-sealing ring; 25-shoulder; 26-high pressure chamber; 27-T-shaped plugs; 28-small head end; 29-fitting grooves; 30-rotating a limiting piece; 31-stator windings; 32-a stator sleeve; 33-connecting plates; 34-a plugging member; 35-locating pins.

Detailed Description

In order that those skilled in the art will better understand the technical solutions of the present invention, preferred embodiments of the present invention will be described below with reference to specific examples, but it should be understood that the drawings are for illustrative purposes only and should not be construed as limiting the present invention; for the purpose of better illustrating the embodiments, certain elements of the drawings may be omitted, enlarged or reduced and do not represent the actual product dimensions; it will be appreciated by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted. The positional relationship described in the drawings are for illustrative purposes only and are not to be construed as limiting the invention.

The invention is further illustrated by the following figures and examples, which are not intended to be limiting.

As shown in fig. 1 to 3, the valve-breaking sleeve spiral positioning guide control type electro-hydraulic proportional servo valve comprises a slide valve assembly 1, an oil port changing plate 2 at the left end of the slide valve assembly 1 and an electric actuator 3 at the right end of the slide valve assembly 1; a spool 4 slidably provided in the axial direction inside the spool valve assembly 1, the spool 4 being partially inserted into the electric actuator 3; the electric actuator 3 is internally and rotatably connected with a pilot stage valve sleeve 5, the pilot stage valve sleeve 5 is connected with a valve core insertion part 7, and the electric actuator 3 can drive the pilot stage valve sleeve 5 to perform radial rotary motion; a pilot structure is arranged between the valve core insertion part 7 and the pilot stage valve sleeve 5, and the pilot structure can convert the rotary motion of the electric actuator 3 into the axial linear motion of the valve core 4.

The slide valve assembly 1 comprises a valve body 8, a main valve sleeve 9 coaxially arranged in the valve body 8 and the valve core 4 coaxially arranged in the main valve sleeve 9; the valve core 4 can axially move along the main valve sleeve 9 in the main valve sleeve 9, the left end of the valve body 8 is fixedly connected with the oil port changing plate 2, and the right end of the valve body 8 is fixedly connected with the electric actuator 3.

As shown in fig. 3, 4 and 6, the electric actuator 3 includes a stator assembly 10, an outer rotor and a motor casing 12, which are coaxially sleeved on the outer side of the pilot valve sleeve 5 in sequence, the motor casing 12 is fixedly connected with the slide valve assembly 1, a connecting plate 33 is sandwiched between the motor casing 12 and the slide valve assembly 1, the stator assembly 10 is fixed on the connecting plate 33, and the outer rotor is fixedly connected with the pilot valve sleeve 5. As shown in fig. 4, the stator assembly 10 includes a stator winding 31 and a stator sleeve 32, and the stator winding 31 is a plurality of copper wires mounted on the stator sleeve 32, that is, copper wires wound on the stator. The stator sleeve 32 is used for protecting and supporting the insulating material of the copper wire, and the stator sleeve 32 can protect the copper wire from being interfered by external mechanical force or electricity, so that the stability and the service life of the motor are improved.

The outer rotor of the electric actuator 3 is composed of a rotary sleeve 13 and a magnetic steel assembly 14 attached to the rotary sleeve 13, the magnetic steel assembly 14 comprises a plurality of magnetic conductive sheets uniformly distributed on the rotary sleeve 13, the rotary sleeve 13 is provided with an annular side wall 15 and an annular base 16 which are integrally formed, a plurality of rib plates 6 are connected between the annular base 16 and the annular side wall 15, the rib plates 6 are arranged to support the annular side wall 15 and simultaneously ensure the heat dissipation function of the electric actuator 3, and the rotary sleeve 13 is fixedly connected with the right end of the pilot stage valve sleeve 5 through the annular base 16, and a positioning pin 35 is arranged between the annular base 16 and the pilot stage valve sleeve 5.

The electric actuator 3 is provided with an axial force bearing assembly, the axial force bearing assembly comprises a first thrust bearing 17 and a second thrust bearing 18, and the pilot stage valve sleeve 5 is arranged between the first thrust bearing 17 and the second thrust bearing 18. As shown in fig. 2, a first thrust bearing 17 is fixed on the main valve sleeve 9, and the first thrust bearing 17 abuts against the left end of the pilot stage valve sleeve 5; a second thrust bearing 18 is fixed to the motor housing 12, the second thrust bearing 18 being in abutment with the right side of the rotating sleeve 13. The rotary sleeve 13 is fixedly connected with the pilot valve sleeve 5, so that the second thrust bearing 18 can cooperate with the first thrust bearing 17 to restrain the pilot valve sleeve 5 from moving in the axial direction, so that the pilot valve sleeve can only perform rotary motion. The axial force bearing assembly ensures stability and accuracy of the pilot stage valve sleeve 5 during movement. The freedom of movement of the pilot stage valve sleeve 5 can be limited effectively, ensuring that its movement in the axial direction is controllable, which is of great importance for the present application.

As shown in fig. 5, the spool insertion portion 7 is provided with a high pressure hole 19 and a low pressure hole 20, the high pressure hole 19 is communicated with a high pressure flow channel (i.e., P port) of the spool valve assembly 1, the low pressure hole 20 is communicated with an inner flow channel 11 of the spool valve 4, the inner flow channel 11 is communicated with a T port of the spool valve assembly 1, the pilot stage valve sleeve 5 is provided with a sensitive cavity channel 21 matched with the high pressure hole 19 and the low pressure hole 20, and the sensitive cavity channel 21 is matched with the high pressure hole 19 and the low pressure hole 20 to form the pilot structure. The sensitive cavity channel 21 and the high pressure hole 19 and the low pressure hole 20 form variable throttle openings respectively, the high pressure hole 19 and the low pressure hole 20 are communicated with the sensitive cavity 23 through the sensitive cavity channel 21, and the two variable throttle openings are connected in series to form a resistance half bridge so as to control the pressure of the sensitive cavity 23.

As shown in fig. 8, the sealing plate 22 is disposed in the pilot stage valve sleeve 5, the sealing plate 22 is disposed on the right side of the sensitive cavity channel 21, and the manner of disposing the sealing plate 22 is opposite to the manner of integrally sealing the tail of the pilot stage valve sleeve 5, so that the overall quality of the servo valve can be reduced, and the power-weight ratio of the servo valve can be improved. The closing plate 22 needs to meet a certain thickness to ensure the stability of the sensitive cavity 23. The right end of the flow channel 11 inside the valve core 4 is provided with a blocking piece 34, and the closing plate 22 and the right end face of the valve core 4 form a sensitive cavity 23 which is only communicated with the sensitive cavity channel 21.

The slide valve assembly 1 comprises a sealing ring 24 coaxially sleeved on the outer side of the valve core 4 and embedded in the main valve sleeve 9, a shoulder 25 is arranged at the left end of the valve core 4, the shoulder 25, the main valve sleeve 9 and the sealing ring 24 form a high-pressure cavity 26 communicated with a high-pressure flow passage of the slide valve assembly 1, and the high-pressure cavity 26 is communicated with the high-pressure flow passage of the slide valve assembly 1.

The slide valve assembly 1 comprises a T-shaped plugging piece 27 abutted against the left end of the main valve sleeve 9 and embedded in the valve body 8, the T-shaped plugging piece 27 is provided with a big head end and a small head end 28 as shown in fig. 9, the main valve sleeve 9 is abutted against the side surface of the big head end, the small head end 28 of the T-shaped plugging piece 27 stretches into the main valve sleeve 9, the end part of the small head end 28 is provided with an assembly groove 29 matched with the valve core 4, the valve core 4 is in sliding connection with the assembly groove 29, and a travel distance L for the axial movement of the valve core 4 is arranged between the valve core 4 and the bottom of the assembly groove 29.

The assembly groove 29 is internally and fixedly provided with a rotation limiting piece 30, and the rotation limiting piece 30 is in sliding connection with the valve core 4. The rotation limiter 30 is a hexagonal prism member, and can limit the rotational movement of the valve element 4.

As shown in fig. 2, the main valve sleeve 9 and the valve body 8 are sequentially provided with a port P, a port a, a port T, a port B and a port P in the axial direction. The system pressure port is a P port, the working oil ports are an A port and a B port, and the oil return pressure port is a T port. When the electric actuator 3 has no control signal, the valve core 4 is at zero position, and the interface area of the high-pressure hole 19 and the low-pressure hole 20 and the sensitive cavity channel 21 is the same. The pressure of the sensitive cavity 23 is half of the system pressure P, while the pressure of the high-pressure cavity 26 is constant at P, at this time, the effective area of the high-pressure cavity 26 is half of the area of the sensitive cavity 23, so that the pressures of the high-pressure cavity 26 and the sensitive cavity 23 are equal (i.e. the hydraulic pressures on the left and right sides of the valve core 4 are equal), and the valve core 4 is in an equilibrium state.

The invention relates to a working process of a valve-breaking sleeve spiral positioning guide control type electrohydraulic proportional servo valve, which comprises the following steps:

after the electric actuator 3 is electrified, the coil on the stator assembly 10 generates a magnetic field and transmits the magnetic field to the magnetic conductive sheet, and under the action of the magnetic field transmitted by the magnetic conductive sheet, the outer rotor is subjected to electromagnetic torque and rotates anticlockwise (as seen from right to left in fig. 2) by a corresponding angle. Under the drive of the rotary sleeve 13, the pilot valve sleeve 5 rotates anticlockwise (as seen from right to left in fig. 2) at the same angle, the junction area of the high-pressure hole 19 and the sensitive cavity channel 21 increases, the junction area of the low-pressure hole 20 and the sensitive cavity channel 21 decreases, the pressure in the sensitive cavity 23 increases, the pressure in the high-pressure cavity 26 is constant, and the valve core 4 moves towards the high-pressure cavity 26 under the action of hydraulic pressure. At this time, the port A is communicated with the port T, the port B is communicated with the port P, the joint area of the sensitive cavity channel 21, the high pressure hole 19 and the low pressure hole 20 is gradually equal in the movement process, the hydraulic pressure born by the valve core 4 is gradually reduced, and the valve core 4 is restored to the balance state after the movement is finished.

In contrast, the outer rotor is subjected to electromagnetic torque and rotated clockwise (as viewed from right to left in fig. 2) by a corresponding angle. Driven by the rotary sleeve 13, the pilot stage valve sleeve 5 rotates clockwise (as seen from right to left in fig. 2) at the same angle, the junction area of the high-pressure hole 19 and the sensitive cavity channel 21 is reduced, the junction area of the low-pressure hole 20 and the sensitive cavity channel 21 is increased, the pressure in the sensitive cavity 23 is reduced, the pressure in the high-pressure cavity 26 is constant, and the valve core 4 moves towards the sensitive cavity 23 under the action of hydraulic pressure. At this time, the port A is communicated with the port P, the port B is communicated with the port T, the joint area of the sensitive cavity channel 21, the high pressure hole 19 and the low pressure hole 20 is gradually equal in the movement process, the hydraulic pressure born by the valve core 4 is gradually reduced, and the valve core 4 is restored to the balance state after the movement is finished.

According to the description of the invention and the accompanying drawings, a broken valve sleeve spiral positioning guide control type electro-hydraulic proportional servo valve can be easily manufactured or used by a person skilled in the art, and the positive effects described by the invention can be produced.

The foregoing description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and any simple modification, equivalent variation, etc. of the above embodiment according to the technical matter of the present invention fall within the scope of the present invention.

Claims (10)

1. A valve-breaking sleeve spiral positioning guide control type electrohydraulic proportional servo valve is characterized in that: the electro-hydraulic proportional servo valve comprises a slide valve component, an oil port changing plate at the left end of the slide valve component and an electric actuator at the right end of the slide valve component; a spool which is slidably provided in the axial direction inside the spool assembly, and a spool portion is inserted into the electric actuator; the electric actuator is internally and rotatably connected with a pilot stage valve sleeve, the pilot stage valve sleeve is connected with a valve core inserting part, and a pilot structure is arranged between the valve core inserting part and the pilot stage valve sleeve.

2. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 1 wherein: the slide valve assembly comprises a valve body, a main valve sleeve coaxially arranged in the valve body and a valve core coaxially arranged in the main valve sleeve; the left end of the valve body is fixedly connected with the oil port changing plate, and the right end of the valve body is fixedly connected with the electric actuator.

3. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 1 wherein: the electric actuator comprises a stator assembly, an outer rotor and a motor cover cylinder which are coaxially sleeved on the outer side of the pilot control stage valve sleeve in sequence, wherein the motor cover cylinder is fixedly connected with the slide valve assembly, a connecting plate is clamped between the motor cover cylinder and the slide valve assembly, the stator assembly is fixed on the connecting plate, and the outer rotor is fixedly connected with the pilot control stage valve sleeve.

4. A valve sleeve screw positioning pilot operated electro-hydraulic proportional servo valve as claimed in claim 3, wherein: the outer rotor consists of a rotary sleeve and a magnetic steel assembly attached to the rotary sleeve, the rotary sleeve is provided with an annular side wall and an annular base which are integrally formed, and the annular base is fixedly connected with the right end of the pilot stage valve sleeve.

5. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 1 wherein: the electric actuator is provided with an axial force bearing assembly, the axial force bearing assembly comprises a first thrust bearing and a second thrust bearing, and the pilot stage valve is sleeved between the first thrust bearing and the second thrust bearing.

6. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 1 wherein: the valve core inserting part is provided with a high-pressure hole and a low-pressure hole, the guide and control stage valve sleeve is provided with a sensitive cavity channel matched with the high-pressure hole and the low-pressure hole, and the sensitive cavity channel is matched with the high-pressure hole and the low-pressure hole to form the guide and control structure.

7. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 6 wherein: and a sealing plate is arranged in the guide and control valve sleeve, the sealing plate is arranged on the right side of the sensitive cavity channel, and the sealing plate and the right end face of the valve core form a sensitive cavity which is only communicated with the sensitive cavity channel.

8. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 2 wherein: the slide valve assembly comprises a sealing ring coaxially sleeved on the outer side of the valve core and embedded in the main valve sleeve, a shoulder is arranged at the left end of the valve core, the shoulder, the main valve sleeve and the sealing ring form a high-pressure cavity communicated with a high-pressure flow passage of the slide valve assembly, and the high-pressure cavity is communicated with the high-pressure flow passage of the slide valve assembly.

9. The valve-breaking sleeve spiral positioning pilot-controlled electrohydraulic proportional servo valve of claim 2 wherein: the slide valve assembly comprises a T-shaped plugging piece which is abutted against the left end of the main valve sleeve and is embedded in the valve body, a small head end of the T-shaped plugging piece extends into the main valve sleeve, an assembly groove matched with the valve core is formed in the end part of the small head end, and a travel distance for the valve core to axially move is formed between the valve core and the groove bottom of the assembly groove.

10. The valve sleeve-breaking spiral positioning pilot-operated electro-hydraulic proportional servo valve as set forth in claim 9, wherein: the assembly groove is internally and fixedly provided with a rotary limiting piece which is in sliding connection with the valve core.