CN212155306U - Electric proportional hydraulic control device for multi-way valve - Google Patents

Abstract

The utility model discloses an electric proportional hydraulic control device for a multi-way valve, which comprises a servo control unit, a driving unit and a servo hydraulic unit, wherein the servo control unit receives an input control signal and outputs a motion state of a control motor according to requirements; the driving unit receives a control motor signal output by the servo control unit and converts the rotary motion of the motor into linear motion; the servo hydraulic unit is used for driving the main valve element of the multi-way valve after amplifying the power of the displacement, speed and other signals provided by the driving unit. The utility model provides a solve and how to realize utilizing motor drive, control a device of hydraulic pressure multichannel switching-over valve, and then solve current electric proportion multiple unit valve and realize with high costs, control algorithm is complicated, the difficult problem of popularizing and applying by a large scale.

Description

Electric proportional hydraulic control device for multi-way valve

Technical Field

The utility model belongs to the technical field of the electro-hydraulic servo control, mainly relate to centralized control's proportion multichannel switching-over valve among the hydraulic system, concretely relates to electricity proportion hydraulic control device for multiple unit valve.

Background

The proportional multi-way reversing valve is a control valve group widely applied to a mobile mechanical hydraulic system, and is formed by adding a proportional function on the basis of the traditional multi-way reversing valve and becomes a direction and flow composite control valve. At present, the control modes of the multi-way valve are generally a direct-acting type and a pilot type, the direct-acting type directly controls the movement of a main valve core of the multi-way valve by changing the angle of a handle, the pilot type directly drives the main valve core of the multi-way valve to move after the pilot type drives the pilot valve core to move after the pilot valve core is converted into hydraulic pressure, and the control pilot valve can adopt a mode of directly controlling through the handle or a mode of controlling an electromechanical conversion mechanism through an electric signal. With the development of electro-hydraulic proportional technology and microelectronic technology, electro-hydraulic proportional multi-way valves using potentiometers, microcomputers and other electrical signal input modes are becoming more and more widespread in recent years.

The common electro-hydraulic proportional multi-way valve has the following structure: the manual reversing valve comprises a valve body with a plurality of reversing units, an electric control module and a manual control module. The reversing units are respectively connected between the oil inlets of the valve body and the corresponding working oil ports; the valve body is also provided with a pilot oil inlet, a pilot oil return port and an oil return port; each reversing unit comprises a main valve core, pilot valves such as an electric proportional pressure reducing valve or a switch valve or a high-speed switch valve are arranged between two control ends of each main valve core and the pilot oil inlet, and the pilot valves, the control unit and the sensing unit LVDT displacement sensor form an electric control module. When the hydraulic control valve works, the pilot valve is controlled to output pilot pressure oil through the switching value or PWM signal output by the electric control unit so as to control the reversing of the main valve core and achieve the purpose of controlling the movement direction and speed of the actuator. The electric proportional hydraulic control structure is high in implementation cost, complex in control algorithm and not easy to popularize and apply in a large area.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide an electricity proportion hydraulic control device for multiple unit valve to solve how to realize utilizing motor drive, control hydraulic pressure multiple directional control valve's problem, and then solve current electricity proportion multiple unit valve and realize with high costs, control algorithm is complicated, the difficult problem of popularizing and applying by a large scale.

In order to solve the problem, the utility model adopts the following technical scheme:

an electric proportional hydraulic control device for a multi-way valve comprises a driving unit and a servo hydraulic unit, wherein the driving unit is used for converting the rotary motion of a motor into linear motion in proportional corresponding relation with the rotary motion, and the servo hydraulic unit is used for amplifying the power of a signal provided by the driving unit and then driving a main valve core of the multi-way valve.

Furthermore, the driving unit comprises a motor and a motion conversion mechanism, the motion conversion mechanism comprises a rotary motion part and a linear motion part which are matched with each other, the linear motion part and the rotary motion part of the motion conversion mechanism are in proportional corresponding relation, the rotary motion part is detachably and fixedly connected with the motor, and the linear motion part is detachably and fixedly connected with the spool of the slide valve.

Furthermore, the periphery of the motion conversion mechanism is provided with a sliding shell for limiting the linear motion part to rotate, two ends of the sliding shell are respectively connected with the motor and the servo hydraulic unit, the motion conversion mechanism is of a screw transmission structure, the rotary motion part is a ball screw, and the linear motion part is a ball nut.

Further, the ball nut is provided with a movable block which is of a polygon prism structure, and the shape of the inner cavity of the sliding shell is matched with the shape of the movable block.

Furthermore, the servo hydraulic unit comprises a control rod, a servo cylinder body, a piston valve sleeve, a valve core assembly and a piston rod fixedly connected with the piston valve sleeve, the piston valve sleeve is connected in the servo cylinder body in a sliding mode and divides the interior of the servo cylinder body into a hydraulic cylinder control rod cavity and a hydraulic cylinder piston rod cavity, the valve core assembly is connected in the piston valve sleeve in a sliding mode, the valve core assembly comprises a slide valve core, one end, located in the hydraulic cylinder control rod cavity, of the slide valve core is detachably and fixedly connected with a linear motion part of the driving unit through the control rod, the piston rod is used for being detachably and fixedly connected with a main valve core of the multi-way valve, the piston rod can follow the linear motion of the control rod, and when the control rod does not provide.

Further, the input of the servo hydraulic unit is a control rod, and the control rod has the following motion states: left and right movements deviating from the middle position, a powered stop state deviating from the middle position, and a free state without power input; the output of the servo hydraulic unit is a piston rod, and the piston rod has the following motion states: the left movement and the right movement of the following control rod deviating from the middle position realize the powered stop state deviating from the middle position along with the control rod, and the following control rod is in a floating state when no power is input.

Further, the utility model discloses still including the servo control unit who is used for controlling drive unit, servo control unit is including control input interface module and the sensor input module that is used for receiving control signal, the central processing unit module that is used for the motor drive module of control motor operation and is used for handling control signal, the acceptable multiple control signal of servo control unit, control drive unit and servo hydraulic unit, and then realize the electric proportional control to the multiple unit valve.

Furthermore, the control input interface module of the servo control unit has one or more of a communication protocol interface, a switching value input interface, a PWM input interface, and an analog input interface, the communication protocol interface is used for receiving digital control signals, the switching value input interface is used for receiving switching value control signals, the PWM input interface is used for receiving PWM control signals, the analog input interface is used for receiving analog input control signals, and the output of the servo control unit is the driving control of the motor, including: the control system comprises the motor, and is characterized by comprising the motor rotation speed control, position control, direction control, electrification stop control and power loss control.

Furthermore, a control input interface of the servo control unit is used as an input of the electric proportional hydraulic control device, a piston rod of the servo hydraulic unit is used as an output of the electric proportional hydraulic control device, and the input and the output of the electric proportional hydraulic control device have the following corresponding relation:

(1) when the control signal input by the servo control unit is zero, the motor is powered off, the output of the servo hydraulic unit is in a floating state, and the main valve core of the multi-way valve returns to the middle position under the action of the main spring;

(2) when the control signal input by the servo control unit is not zero and does not change, the output state of the servo hydraulic unit is as follows: the main valve core of the multi-way valve is in a corresponding position deviated from the middle position when the main valve core of the multi-way valve stops moving after moving to a position corresponding to the control signal;

(3) when the control signal input by the servo control unit is not zero and changes, the output state of the servo hydraulic unit is as follows: the main valve core of the multi-way valve moves by a distance corresponding to the variable quantity of the control signal, and the main valve core of the multi-way valve moves forwards or backwards by a distance corresponding to the variable quantity of the input control signal from the current position.

Further, the servo control unit and the motor can be integrally installed, and the servo control unit and the motor can also be separately installed through cable connection.

Furthermore, the motor can be selected to be provided with an encoder, the encoder outputs motor speed and angular displacement signals to the servo control unit, and the servo control unit completes accurate proportional control of the multi-way reversing valve.

Adopt above-mentioned technical scheme, the utility model has the advantages of it is following:

1. the multi-way valve electric control device is low in cost, the rotary motion of the motor is converted into linear reciprocating motion by the aid of the driving unit, the servo hydraulic unit is used as power assistance to drive the main valve core of the multi-way valve, the high-speed valve or the proportional valve which is expensive relatively, and the LVDT sensor is used for forming the multi-way valve electric control device, and the cost is greatly reduced.

2. Control accuracy is high, the technical scheme of the utility model the moving speed that can decide main valve core according to the rotational speed of motor is fast slow, decides main valve core's position according to the angle of motor rotation, and servo hydraulic unit follows drive unit's removal completely, and main valve core's removal displacement relies on the helical pitch of lead screw or the machining precision decision of pitch, makes the control accuracy of multichannel valve high.

3. Compatibility is better, and control is simple, the utility model discloses an electricity proportional hydraulic control device when using in the multiple unit valve, its servo control unit provides multiple control signal input interface, include: digital input interface, switching value input interface, analog input interface, PWM input interface, for the host computer is equivalent to control 2 electro-magnets.

To sum up, the utility model has the advantages of realize with low costs, control method is simple, the reaction is quick, reliable, compatible good, can create the condition for the technological transformation of various old machines, easily the large tracts of land is popularized and applied.

Drawings

Fig. 1 is a schematic exploded view of the present invention;

FIG. 2 is a schematic structural diagram of the multi-way valve of the present invention;

FIG. 3 is a schematic view of the structure of the present invention;

fig. 4 is a schematic sectional structure of the present invention;

fig. 5 is a block diagram of a servo control unit according to the present invention;

fig. 6 is a control schematic diagram of the servo control unit of the present invention;

fig. 7 is a software control flow chart of the servo control unit according to the present invention;

FIG. 8 is a schematic perspective view of a piston valve sleeve in the servo hydraulic unit;

FIG. 9 is one of schematic cross-sectional structural views of the servo hydraulic unit;

FIG. 10 is a second schematic sectional view of the servo hydraulic unit;

FIG. 11 is a schematic diagram of forward servo control of the motor according to the present invention;

fig. 12 is a schematic view of the motor stop servo control of the present invention;

fig. 13 is a schematic view of the motor reverse servo control of the present invention;

fig. 14 is a schematic diagram of the servo control for power loss of the motor of the present invention.

Reference numerals:

1. the multi-way valve is connected in a working way; 2. a manual operating device; 3. a drive unit; 4. a servo hydraulic unit; 5. a multi-way valve cover plate; 6. the multi-way valve is connected with an oil inlet; 7. servo control unit

11. A valve body; 12. a main valve element;

21. a manual operating device housing; 22. a main spool return spring;

31. a motor; 32. a ball screw; 33. a ball nut; 34. a sliding shell; 35. a moving block; 36. a bearing cover plate; 37. a motor mounting plate;

41. a servo cylinder; 411. a hydraulic cylinder control rod cavity; 412. a hydraulic cylinder piston rod cavity; 42. a piston valve housing; 421. a flat bond; 43. a spool valve core; 441. a spool return spring; 442. a spring seat; 45. a piston left end cover; 46. a piston right end cover; 461. a spool receiving groove; 462. a piston rod; 47. a servo cylinder front cylinder cover; 48. a servo cylinder rear cylinder cover; 49. a control lever; 491. a control lever connecting part; 492. a valve core connecting portion; 493. a position avoiding part;

71. a control input interface module; 711. a communication protocol interface; 712. a switching value input interface; 713. a PWM input interface; 714. an analog input interface; 72. a central processor module; 73. a motor drive module; 74. a sensor input module; 75. a power supply module;

s1, a data interface input management module; s2, a data processing module; s3, a motor drive management module;

s21, a digital quantity data processing module; s22, a switching value data processing module; s23, a PWM data processing module; s24, an analog quantity data processing module; s25, a sensor data processing module; s26, a motor open-loop control quantity calculation module; and S27, a motor closed-loop control quantity calculation module.

Detailed Description

In order to make the technical objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be further described with reference to fig. 1 to 14 and specific embodiments, in which the direction in which the spool of the slide valve moves toward the driving unit is the left direction, and the direction in which the spool of the slide valve moves away from the driving unit is the right direction.

The utility model discloses mainly use in the multiple unit valve, control the main valve core in the multiple unit valve, as shown in fig. 2, the multiple unit valve generally has the valve body 11 of a plurality of switching-over units, and every switching-over unit all contains a main valve core 12, and manual control device 2 is installed to main valve core 12's one end, and a set of is all installed to every main valve core 12's the other end the utility model discloses an electricity proportion hydraulic control device. Valve body 11 includes that the multi-way valve work allies oneself with 1, multi-way valve apron 5 and multi-way valve oil feed allies oneself with 6, and the multi-way valve work allies oneself with 6 and manual controlling device 2 with the multi-way valve oil feed and is prior art, can adopt the general product in market, specifically no longer gives details, valve body 11 through change after all can with electric proportional control hydraulic pressure multi-way valve is formed in the use to the cooperation of electricity proportional control hydraulic pressure hydraulic control device.

As shown in fig. 1 to 4, the electro-proportional hydraulic control apparatus includes a driving unit 3 for converting a rotational motion of a motor into a linear motion in a proportional correspondence relationship with the rotational motion, and a servo hydraulic unit 4 for amplifying a power of a signal (e.g., a displacement, a speed, a power-on stop, a power-off signal, etc.) provided by the driving unit 3 and driving a main spool 12 of a multi-way valve.

Further, as shown in fig. 1 and 4, the driving unit 3 technology is implemented as follows:

the driving unit 3 comprises a motor 31 and a motion conversion mechanism, the motor 31 adopts a micro motor 31 to reduce the installation size, the motor 31 is connected with a motor driving module, and can be integrated with the motor 31, the motor driving module is the prior conventional technology, details are not repeated, the motion conversion mechanism can be a screw transmission structure, a gear rack transmission structure, a worm and gear transmission structure and the like which convert rotary motion into linear motion, the motion conversion mechanism comprises a rotary motion piece and a linear motion piece which are matched with each other, the linear motion of the motion conversion mechanism corresponds to the rotary motion in proportion, the rotary motion piece is detachably and fixedly connected with the motor 31, and the linear motion piece is detachably and fixedly connected with the spool valve 43 of the slide valve through a control rod. In this embodiment, a screw transmission structure is adopted, the rotary motion member is a ball screw 32, and the linear motion member is a ball nut 33.

Further, a sliding shell 34 for limiting the rotation of the linear motion part is arranged on the periphery of the motion conversion mechanism, two ends of the sliding shell 34 are respectively connected with the motor 31 and the servo hydraulic unit 4, a moving block 35 is detachably and fixedly connected to the ball nut 33, the moving block 35 serves as the linear motion part, the moving block 35 is of a polygon prism structure, the shape of an inner cavity of the sliding shell 34 is matched with the shape of the moving block 35, when the cross section of the moving block 35 is square, the cross section of the inner cavity of the sliding shell 34 is also square, and the moving block 35 can only reciprocate in the sliding shell 34 and cannot rotate.

Further, bearing cover plate 36 is installed to the tip of shell 34 that slides, install motor mounting panel 37 between bearing cover plate 36 and the motor 31, motor 31 is installed on motor mounting panel 37, the motor shaft mounting groove has been seted up to ball 32's one end, the rotation axis tip of motor 31 inserts in the motor shaft mounting groove and is connected with ball 32, ball 32's one end is passed through the bearing and is rotated and connect in bearing cover plate 36, ball 32 passes through bearing cover plate 36 and installs the jump ring axial fixity in bearing cover plate 36.

Further, as shown in fig. 1 and 4, the main function of the servo hydraulic unit 4 is to follow the displacement and speed of the square moving block 35 of the driving unit 3 and perform power amplification to drive the multi-way valve main spool 12.

The servo hydraulic unit 4 technology is realized as follows:

the servo hydraulic unit 4 includes a control rod 49, a servo cylinder 41, a piston valve sleeve 42, a valve core assembly, a piston rod 462, the valve core assembly is slidably connected in the piston valve sleeve 42, the piston valve sleeve 42 is slidably connected in the servo cylinder 41 and divides the interior of the servo cylinder 41 into a cylinder control rod chamber 411 and a cylinder piston rod chamber 412. The valve core assembly is connected in the piston valve sleeve 42 in a sliding manner, the valve core assembly comprises a slide valve core 43 and a slide valve centering spring resetting device, one end of the slide valve core 43, which is positioned in the hydraulic cylinder control rod cavity 411, is detachably and fixedly connected with the square moving block 35 of the driving unit 3, and one end of the piston valve sleeve 42, which is positioned in the hydraulic cylinder piston rod cavity 412, is connected with the multi-way valve main valve core 12 by using a piston rod 462; the piston rod 462 is able to follow the linear movement of the drive unit 3 and the piston valve sleeve 42 and the piston rod 462 are in a free floating state when no linear movement is provided by the drive unit 3.

The input of the servo hydraulic unit 4 is a control rod 49, one end of the spool valve 43 located in the control rod cavity of the hydraulic cylinder is detachably and fixedly connected with the linear motion part of the driving unit 3 through the control rod 49, and the control rod 49 has the following motion states: left and right movements deviating from the middle position, a powered stop state deviating from the middle position, and a free state without power input; the output of the servo hydraulic unit 4 is a piston rod 462, the piston rod 462 having the following motion states: following the leftward and rightward movement of the lever 49 away from the neutral position, the power-driven stop state away from the neutral position is realized by the lever 49, and the lever 49 is in a floating state when no power is input.

Further, according to the motion state requirement corresponding to the input and output of the servo hydraulic unit 4, the spool valve 43 and the piston valve sleeve 42 are designed in a slide valve type structure, and further the slide valve is designed in a five-position four-way reversing valve structure, five positions of the slide valve type five-position four-way reversing valve are respectively a middle position, a left stop position, a left reversing position, a right stop position and a right reversing position, so that the piston valve sleeve assembly can be ensured to be in a floating state when the servo hydraulic unit loses power at the control rod 49, and to be in a middle position under the action of a main valve core reset spring of the multi-way valve.

As shown in fig. 9, an oil inlet P3, an oil return port T3, a control oil port a3 and a control oil port b3 are arranged in the piston valve sleeve 42, the control oil port a3 is communicated with the hydraulic cylinder control rod cavity 411 through an oil passage, the control oil port b3 is communicated with the hydraulic cylinder piston rod cavity 412, and when the spool valve 43 reciprocates in the piston valve sleeve 42, the oil inlet P3, the oil return port T3, the control oil port a3 and the control oil port b3 are communicated or closed through the matching of the spool valve 43 and the piston valve sleeve 42.

As shown in fig. 4 and 9, further, five undercut grooves for communicating oil are formed in the piston valve sleeve 42, the oil inlet P3, the oil return port T3, the control oil port a3 and the control oil port b3 are respectively formed in different undercut grooves, the spool 43 of the spool valve is provided with three shoulders for opening or closing the oil ports, and when the spool 43 of the spool valve reciprocates in the piston valve sleeve 42, the undercut grooves are opened or closed by the shoulders on the spool 43 of the spool valve, so that the oil ports communicated with the undercut grooves are opened or closed; the oil inlet P3 is of a negative opening type, the oil return port T3 is of a positive opening type, when the slide valve type five-position four-way reversing valve is of a middle position, the oil inlet P3 is cut off, the control oil port a3, the control oil port b3 and the oil return port T3 are communicated, the covering amount of the oil inlet P3 is larger than or equal to the opening amount of the oil return port T3, and the flow rate of the slide valve type five-position four-way reversing valve is controlled through the opening amount of the valve port corresponding to each control edge.

The slide valve type five-position four-way reversing valve is defined as follows:

when the oil inlet is in a middle position, the oil inlet P3 is cut off, and the control oil port a3, the control oil port b3 and the oil return port T3 are communicated;

when the left stop position is reached, the oil inlet P3 is cut off, the control oil port a3 is cut off, and the control oil port b3 is communicated with the oil return port T3;

when the direction is changed leftwards, the oil inlet P3 is communicated with the control oil port a3, and the control oil port b3 is communicated with the oil return port T3;

when the oil inlet is stopped at the right stop position, the oil inlet P3 is stopped, the control oil port b3 is stopped, and the control oil port a3 is communicated with the oil return port T3;

when the direction of the oil inlet is changed rightwards, the oil inlet P3 is communicated with the control oil port b3, and the control oil port a3 is communicated with the oil return port T3.

Further, fixedly connected with piston left end cover 45 can be dismantled to piston valve barrel 42's one end, fixedly connected with piston right end cover 46 can be dismantled to piston valve barrel 42's the other end, piston left end cover 45 and piston right end cover 46 can be threaded connection at piston valve barrel 42's both ends respectively, cylinder cover 47 before the servo cylinder of fixedly connected with can be dismantled to servo cylinder 41's one end, cylinder cover 48 behind the servo cylinder of fixedly connected with can be dismantled to servo cylinder 41's the other end, form between piston left end cover 45 and the servo cylinder cover 47 the pneumatic cylinder control rod chamber 411, form between piston right end cover 46 and the servo cylinder cover 48 pneumatic cylinder piston rod chamber 412.

Furthermore, at least one control oil hole a2 is opened on the piston left end cover 45, the control oil hole a3 is communicated with the hydraulic cylinder control rod cavity 411 through a control oil hole a2, at least one control oil hole b2 is opened on the piston right end cover 46, and the control oil hole b3 is communicated with the hydraulic cylinder piston rod cavity 412 through a control oil hole b 2.

The spool valve centering spring return means may be mounted at either or both ends of the spool 43 of the spool valve, which, in this embodiment, the slide valve centering spring resetting device is arranged at one end of the slide valve spool 43 close to the driving unit 3, specifically, a stepped hole is arranged on the piston left end cover 45, one end of the control rod 49 is connected in the stepped hole in a sliding manner, the stepped hole comprises a fine hole section and a coarse hole section, the slide valve centering spring resetting device is arranged at the coarse hole section of the stepped hole, the slide valve centering spring resetting device comprises a slide valve resetting spring 441 and two spring seats 442, the two spring seats 442 are connected in the coarse hole section in a sliding manner, and the slide valve resetting spring 441 is in a natural state, the end surface of one of the spring seats 442 abuts against the end surface of the coarse hole section, the end surface of the other spring seat 442 abuts against the shoulder end surface of the spool valve 43, and the distance between the two spring seats 442 is the maximum relative displacement of the spool valve 43 with respect to the piston valve sleeve 42.

Further, the spool return spring 441 of the spool centering spring return device has a stiffness less than that of the main spool return spring 22. When the motor 31 is de-energized, the piston valve sleeve 42 of the servo hydraulic unit 4 is in a floating state under the action of the slide valve return spring 441, and the action of the main valve core manual control device 2 is not influenced.

When the control rod 49 has power input, the position of the spool valve 43 is determined by the control rod 49, when the control rod 49 has no motion input, the position of the spool valve 43 returns to the neutral position under the action of the spool centering spring return device, namely, when the spool valve 43 moves rightwards under the drive of the control rod 49, the control rod 49 pushes the left spring seat 442 to move rightwards, the spool valve return spring 441 is compressed, and when the control rod 49 has no motion input, the spool valve 43 moves leftwards to return to the neutral position under the action of the spool valve return spring 441; when the spool valve 43 moves leftward by the operation lever 49, the land on the spool valve 43 pushes the right spring seat 442 leftward, the spool return spring 441 is compressed, and when there is no motion input to the operation lever 49, the spool valve 43 moves rightward by the spool return spring 441 to return to the neutral position.

As shown in fig. 1 and 8, four regions are provided between the piston valve sleeve 42 and the servo cylinder 41 in the servo hydraulic unit 4, which are a circumferential isolation region at both ends, an anti-rotation groove region, two oil groove regions that are not communicated with each other, and an axial isolation region that separates the two oil groove regions, where the two oil groove regions are respectively used as an oil inlet groove and an oil return groove, and the axial dimension of the oil inlet groove and the oil return groove is set to be greater than the stroke of the piston valve sleeve 42, so as to ensure that the oil inlet groove is always communicated with an oil inlet passage and the oil return groove is always communicated with an oil return passage in the moving process of the piston valve sleeve 42.

The piston valve sleeve 42 and the servo cylinder 41 are respectively provided with an anti-rotation groove in an anti-rotation groove area, a flat key 421 is arranged between the two anti-rotation grooves, and the piston valve sleeve 42 and the servo cylinder 41 are connected through the flat key 421; during installation, the flat key 421 can be fixed in the anti-rotation groove of the piston valve sleeve 42 by a screw, then the piston valve sleeve 42 with the flat key 421 is installed in the servo cylinder 41, the flat key 421 can circumferentially restrict the piston valve sleeve 42, and the piston valve sleeve 42 can only reciprocate along the axial direction of the servo cylinder 41 and cannot rotate.

Further, as shown in fig. 10, a pilot oil inlet P1 and a pilot oil return port T1 are provided on the servo cylinder 41, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are provided between the piston valve housing 42 and the servo cylinder 41 along the axial direction, the oil inlet groove P2 and the oil return groove T2 may be opened on the outer periphery of the piston valve housing 42 or on the inner wall of the servo cylinder 41, the oil inlet P3 of the piston valve housing 42 is communicated with the pilot oil inlet P1 through the oil inlet groove P2, the oil return port T3 of the piston valve housing 42 is communicated with the pilot oil return port T1 through the oil return groove T2, the oil inlet groove P2 is always communicated with the pilot oil inlet P1, and the oil return groove T2 is always communicated with the pilot oil return port T1 during the movement of the.

The pilot oil return port T1 on the servo cylinder 41 may be connected to the pilot oil return port on the valve body 11 through an external or internal oil passage, the pilot oil inlet P1 on the servo cylinder 41 may be connected to the pilot pressure reducing valve oil outlet on the multi-way valve oil inlet link 6 or the pilot oil pump oil outlet independent of the multi-way valve through an external or internal oil passage, and the related oil passages of the multi-way valve body 11 are all the existing mature technologies, and are not described herein again.

Further, the electro-proportional hydraulic control device further comprises a servo control unit 7 for receiving the control signal, performing logical operation on the control signal, and outputting the control signal to control the motor, wherein the servo control unit 7 is implemented as follows:

as shown in fig. 5, the hardware of the servo control unit 7 includes a control input interface module 71 and a sensor input module 74 for receiving control signals, a motor driving module 73 for controlling the operation of the motor, a central processor module 72 for processing the control signals, and a power supply module 75 for supplying power, and the servo control unit 7 can receive various control signals, control the driving unit and the servo hydraulic unit, and further implement the electric proportional control of the multi-way valve. The structures and working principles of the control input interface module 71, the sensor input module 74, the motor driving module 73, the central processor module 72 and the power supply module 75 are the prior art, and are not described in detail again.

Further, the control input interface module 71 of the servo control unit includes one or more of a communication protocol interface 711, a switching value input interface 712, a PWM input interface 713, and an analog input interface 714, which will be described in detail below. The output of the servo control unit is the drive control of the motor, comprising: the control system comprises the motor, and is characterized by comprising the motor rotation speed control, position control, direction control, electrification stop control and power loss control.

The communication protocol interface 711 is used for receiving a digital control signal, the size of the digital signal represents the degree of the opening of the valve port of the multi-way valve deviating from the middle position, the sign represents the direction of the opening of the valve port of the multi-way valve deviating from the middle position, power loss or control data are zero, and the main valve core of the multi-way valve can freely return to the middle position.

The switching value input interface 712 is used to receive a switching value control signal. Further, the servo control unit 7 uses 2 switching value inputs, the switching value is 1, and the multi-way valve is at the extreme position; when power is lost or control data is zero, the main valve core of the multi-way valve can freely return to the middle position, and the 2-way switching value can represent that the valve port of the multi-way valve is left-opened or right-opened.

The PWM input interface 713 is for receiving a PWM control signal. After receiving the PWM control signal, the PWM input interface 713 controls the driving unit and the servo hydraulic unit to further realize the electrical proportional control of the multi-way valve, further, the servo control unit 7 utilizes 2-way PWM input, where PWM is greater than or equal to 0, and is less than or equal to 1, where PWM is a decimal number indicating that the multi-way valve is at a certain position, and PWM is 1 indicating that the multi-way valve is at an extreme position; when power is lost or control data is zero, the main valve core of the multi-way valve can freely return to the middle position, and 2-way PWM can represent that the valve port of the multi-way valve is opened left or right.

The analog input interface 714 is configured to receive an analog input control signal, which includes a selectable 0-5v or 0-12v voltage input, or a 4-20 ma current input, and receive the analog input control signal, further, the servo control unit 7 uses 2 paths of analog inputs, where the analog magnitude represents a degree of deviation of the opening of the multi-way valve port from a middle position, the 2 paths of analog inputs represent left deviation or right deviation of the multi-way valve port, respectively, the power loss or control data is zero, and the main spool of the multi-way valve can freely return to the middle position.

Further, as shown in fig. 6, the control portion of the central processor module 72 includes a data interface input management module S1, a data processing module S2, a motor drive management module S3, and further the data processing module S2 includes: a digital quantity data processing module S21, a switching value data processing module S22, a PWM data processing module S23, an analog quantity data processing module S24, a sensor data processing module S25, a motor open-loop control quantity calculating module S26, a motor closed-loop control quantity calculating module S27 and the like; the data interface input management module S1 mainly implements preprocessing of input data and screening of data types, the data processing module S2 calls different data processing modules according to different types of data, and the processed data calls the motor drive management module S3 to control the operating state of the motor.

Further, as shown in fig. 7, the data processing method of the electro-proportional hydraulic control device for the multi-way valve as described above includes the following steps:

(1) and judging whether an input signal exists or not through the data interface input management module S1 in the central processing unit module, if no, controlling the motor by the motor drive management module S3 in the central processing unit module, enabling the main valve core of the multi-way valve to freely return to the middle position, and if so, entering the next step.

(2) Judging the type of the input signal through a data interface input management module S1 in the central processing unit module, judging whether the input signal is a digital quantity, if so, processing the input digital control signal through a digital quantity data processing module S21 and an open-loop control quantity calculation module S26 in the central processing unit module, calling a motor drive management module S3 by the processed data, and controlling the running state of the motor through a motor drive module 73; if not, the next step is carried out.

The servo control unit 7 is provided with a communication protocol interface 711, receives a digital control signal sent by an upper computer, because the multi-way directional valve needs to be in a middle position when losing driving force, optionally, ranges [0, a ] and [ -a, 0] of the digital control signal can be set, a corresponds to the main valve core of the multi-way valve being in a left limit position, a corresponds to the main valve core of the multi-way valve being in a right limit position, the central processor module 72 can represent the rotation direction of the motor according to the sign of the digital control signal, the value represents the position, and meanwhile, the rotation speed of the motor can be set so as to control the dynamic response characteristic of the multi-way directional valve, and after logical operation, the drive unit and the servo hydraulic unit are controlled, so that the electric proportional control of the multi-.

(3) Judging whether the input signal type is a switching value through a data interface input management module S1 in the central processing unit module, if so, processing the input switching value control signal through a switching value data processing module S22 and an open-loop control value calculation module S26 in the central processing unit module, calling a motor drive management module S3 by the processed data, and controlling the running state of the motor through a motor drive module 73; if not, the next step is carried out.

The servo control unit 7 includes a switching value input interface 712, and receives a switching value control signal, and the method includes: optionally two switching value control signals may be provided: a = {0 OR 1}, b = {0 OR 1}, when a control parameter a =1, the motor rotates forward to the limit position corresponding to the main valve core of the multi-way valve being at the left limit position, when b =1, the motor rotates backward to the limit position corresponding to the main valve core of the multi-way valve being at the right limit position, when a = b =0, the motor loses power corresponding to the main valve core of the multi-way valve being at the middle position, the central processor module 72 can represent the rotation direction of the motor and the Boolean value representing position according to the control quantities a and b, and can set the rotation speed of the motor to control the dynamic response characteristic of the multi-way reversing valve, and after logical operation, the driving unit and the servo hydraulic unit are controlled, so that the switching amount control of the multi-way valve is realized.

(4) Judging whether the input signal type is PWM or not through a data interface input management module S1 in the central processing unit module, if so, processing the input PWM control signal through a PWM data processing module S23 and an open-loop control quantity calculation module S26 in the central processing unit module, calling a motor drive management module S3 by the processed data, and controlling the running state of the motor through a motor drive module 73; if not, the next step is carried out.

The servo control unit 7 includes a PWM input interface 713, and receives a PWM control signal, and the method includes: optionally two PWM control signals may be provided: a = PWM1, b = PWM2, the central processor module 72 processes the signal according to the PWM module to obtain the duty ratio of the parameters a, b, the duty ratio is between 0-1, when the control parameter a =1, the motor rotates forward to the limit position corresponding to the main valve core of the multi-way valve being at the left limit position, when the control parameter b =1, the motor rotates backward to the limit position corresponding to the main valve core of the multi-way valve being at the right limit position, when a = b =0, the motor loses power, the main valve core of the multi-way valve is at the middle position, the central processor module 72 can represent the rotation direction of the motor according to the category of the control quantity a, b, if a or b is decimal, any position between the middle position and the limit position is represented, meanwhile, the rotation speed of the motor can be set to control the dynamic response characteristic of the multi-way reversing valve, the central processor controls the driving unit and the servo hydraulic, and further realizing proportional servo control on the multi-way valve.

(5) Judging the type of the input signal through a data interface input management module S1 in the central processing unit module, judging whether the input signal is an analog quantity, if so, processing the input signal through an analog quantity data processing module S24 and an open-loop control quantity calculation module S26 in the central processing unit module, calling a motor drive management module S3 by the processed data, and controlling the running state of the motor through a motor drive module 73; if not, the next step is carried out.

The servo control unit 7 is provided with an analog input interface 714, comprises a voltage input of 0-5v or 0-12v, or a current input of 4-20 milliamperes, and receives an analog input control signal, and the method comprises the following steps: optionally two analog input signals may be provided: a = [0, 5V ], b = [0, 5V ], where a =5, b =0 is a control parameter, where forward rotation of the motor to the limit position corresponds to the multi-way valve main spool being at the left limit position, b =5, a =0 is a control parameter, reverse rotation of the motor to the limit position corresponds to the multi-way valve main spool being at the right limit position, and when a = b =0 is a control parameter, the motor is de-energized and corresponds to the multi-way valve main spool being at the center position, the central processor module 72 may represent a motor rotation direction according to the category of the control quantity a, b or a is any value [0, 5V ], and another parameter b or a must be 0 and represents any position between the center position and the limit position, and may set a rotation speed of the motor to control a dynamic response characteristic of the multi-way reversing valve, and the central processor controls the driving unit and the servo hydraulic unit after logical operation, and further realizing proportional servo control on the multi-way valve.

(6) Judging whether a sensor is input or not through a data interface input management module S1 in the central processing unit module, if so, processing an input sensor control signal through a sensor data processing module S25 and a closed-loop control quantity calculation module S27 in the central processing unit module, calling a motor drive management module S3 by the processed data, and controlling the running state of the motor through a motor drive module 73; if not, the next step is carried out.

(7) And (5) repeating the steps (1) to (6).

Further, the servo control unit 7 may be integrally installed with the motor or separately installed through cable connection.

Further, the motor 31 can be selected to be provided with an encoder, the encoder outputs a motor speed and an angular displacement signal to the servo control unit 7, and the servo control unit 7 completes the accurate proportional control of the multi-way reversing valve.

Further, as an application example of the present invention, the control process is as follows:

when the motor in the driving unit 3 rotates forwards or reversely, the spool valve 43 in the servo hydraulic unit 4 extends or retracts following the action of the linear motion part in the driving unit 3, so that the spool valve 43 and the spool valve 42 form a spool valve port which is opened, hydraulic oil forces the spool valve 42 to move towards the direction of closing the valve port, thereby following the movement of the spool valve 43, and the main valve 12 extends or retracts following the action of the spool valve 42;

when the motor in the driving unit 3 stops rotating with electricity, the spool valve 43 in the servo hydraulic unit 4 stops moving, the piston valve sleeve 42 closes the spool valve port under the action of hydraulic oil, the piston valve sleeve 42 in the servo hydraulic unit 4 stops moving and cannot move continuously, and the main spool 12 can stop at any position in the stroke;

when the motor in the driving unit 3 is powered off, the servo hydraulic unit 4 is under the action of the spool valve centering spring return device, the spool valve composed of the spool valve 43 and the piston valve sleeve 42 is in the neutral position, the piston valve sleeve 42 is in the floating state, under the action of the restoring force of the main spool return spring 22, the main spool 12 returns to the neutral position, and the piston valve sleeve 42 returns to the neutral position.

The speed of the motor in drive unit 3 determines the speed of movement of main spool 12, and the angle of rotation of the motor in drive unit 3 determines the position of main spool 12.

The normal rotation direction of the motor 31 is defined as the direction in which the ball nut 33 moves toward the motor 31, and the reverse rotation direction is defined as the reverse rotation direction.

As shown in fig. 11, assuming that the input signal received by the servo control unit 7 is a digital control signal, and the digital control signal is greater than zero, the motor 31 is controlled to rotate forward, the motor 31 drives the spool valve 43 to move continuously, at this time, the slide valve type five-position four-way reversing valve is in the right reversing position, that is, the oil inlet P3 is communicated with the control oil port b3, and the right oil return port T3 of the slide valve type five-position four-way reversing valve is in the closed state, the hydraulic cylinder piston rod chamber 412 continuously feeds oil, pushes the piston valve sleeve 42 to be closed continuously and the opening of the spool valve 43, and follows the movement of the spool valve 43, so that the main spool of the multi-way reversing valve can move leftward, and opens the right.

As shown in fig. 12, assuming that the digital control signal received by the servo control unit 7 is not changed, the motor 31 stops rotating with electricity, because at the moment of stopping, the spool valve 43 is in the right direction change, the oil in the cylinder piston rod cavity 412 is still not fed, the spool valve 43 has stopped moving, the piston valve sleeve 42 continues moving, the oil inlet P3 is closed, the oil is stopped, the oil return port T3 on the right side of the spool valve 43 is in the closed state, at this time, the spool valve 43 is in the right stop position, the cylinder piston rod cavity 412 is closed, the spool valve formed by the spool valve 43 and the piston valve sleeve 42 cannot return to the center position, and the main spool 12 of the multi-way valve is in a certain opening position of.

As shown in fig. 13, assuming that the digital control signal received by the servo control unit 7 is greater than zero and the digital signal becomes smaller, the motor 31 starts to reverse from the charged stop, the spool 43 is displaced from the right stop position to the middle position, i.e., the spool 43 moves rightward, at this time, the oil inlet P3 continues to be in the stop state, but the oil return port T3 is opened, and enters the middle position, the cylinder lever cavity 411 and the cylinder rod cavity 412 both open through the oil return port T3, at this time, the piston rod 462 pushes the piston valve housing 42 to retreat, i.e., the piston valve housing 42 follows the spool 43 to move rightward under the external force, e.g., the action of the main spool return spring 22 of the multi-way valve main valve, so as to continuously close the opening of the oil return port T36.

Assuming that the digital control signal received by the servo control unit 7 becomes smaller and no change occurs, the motor 31 executes a command and then stops rotating with electricity, the motor 31 stops rotating reversely, the spool valve 43 stops moving, the piston valve sleeve 42 continues to move to close the opening of the right oil return port T3, the spool valve 43 is at the right stop position, the piston valve sleeve 42 stops withdrawing, the piston rod cavity 412 of the hydraulic cylinder is closed, the spool valve formed by the spool valve and the piston valve sleeve cannot return to the middle position, and at this time, the main spool 12 of the multi-way valve also stops withdrawing.

As shown in fig. 14, assuming that the digital control signal received by the servo control unit 7 is zero, the servo control unit 7 outputs a control signal to control the motor 31 to lose power, after the motor 31 loses power, the spool valve 43 overcomes the positioning torque of the motor 31 (in this embodiment, the micro stepper motor 31 is used) under the action of the spool valve return spring 441 (i.e., the torque required for rotation under the action of external force when the motor 31 loses power), the motor 31 loses power and reverses, the spool valve 43 returns to the neutral position, at this time, the cylinder lever cavity 411 and the cylinder piston rod cavity 412 are respectively communicated with the oil return port T3, the piston valve sleeve 42 is in a floating state, under the action of the restoring force of the multi-way valve main spool return spring 22, the multi-way valve main spool 12 returns to the neutral position, the piston valve sleeve 42 of the servo hydraulic unit 4 returns to the neutral position, and.

On the contrary, if the digital control signal received by the servo control unit 7 is smaller than zero, the control motor 31 starts to be electrified and reversely rotated, the basic principle and the control process of the control motor are the same as those of the motor 31 when being electrified and positively rotated, the main valve core of the multi-way reversing valve can be moved rightwards, and the left reversing position of the main valve of the multi-way reversing valve is opened; when the motor 31 rotates from the charged state to the stopped state, the spool valve element 43 is at the left stop position, and the multi-way valve main spool 12 is at an opening position of the left stop position.

The utility model discloses in used hydraulic pressure symbol (like oil inlet P3, oil return T3, control hydraulic fluid port a3, control hydraulic fluid port b3 etc.) only in order to distinguish each control hydraulic fluid port, it is not right the utility model discloses a technical scheme's restriction, and above-mentioned embodiment are not right the utility model discloses a shape, material, structure etc. do the restriction on any form, all the basis the utility model discloses a technical essence is to any simple modification, the equivalent change and the modification of making above embodiment, all belong to the utility model discloses technical scheme's protection scope.

Claims (8)

1. An electro-proportional hydraulic control apparatus for a multi-way valve, characterized by: the multi-way valve comprises a driving unit and a servo hydraulic unit, wherein the driving unit is used for converting the rotary motion of a motor into linear motion in proportional corresponding relation with the rotary motion, and the servo hydraulic unit is used for amplifying the power of a signal provided by the driving unit and then driving a main valve core of the multi-way valve.

2. The electro-proportional hydraulic control device for the multi-way valve as claimed in claim 1, wherein: the servo hydraulic unit comprises a control rod, a servo cylinder body, a piston valve sleeve, a valve core assembly and a piston rod fixedly connected with the piston valve sleeve, the valve core assembly comprises a slide valve core, two ends of the control rod are respectively connected with the driving unit and the slide valve core, the piston rod can follow the linear motion of the control rod, and the piston valve sleeve and the piston rod are in a free floating state when the control rod does not provide the linear motion.

3. The electro-proportional hydraulic control device for the multi-way valve as claimed in claim 2, wherein: the input of the servo hydraulic unit is an operating rod, one end of a spool valve of the sliding valve is detachably and fixedly connected with a linear motion part of the driving unit through the operating rod, and the operating rod has the following motion states: left and right movements deviating from the middle position, a powered stop state deviating from the middle position, and a free state without power input; the output of the servo hydraulic unit is a piston rod, and the piston rod has the following motion states: the left movement and the right movement of the following control rod deviating from the middle position realize the powered stop state deviating from the middle position along with the control rod, and the following control rod is in a floating state when no power is input.

4. The electro-proportional hydraulic control device for the multi-way valve as claimed in claim 2, wherein: the driving unit comprises a motor and a motion conversion mechanism, the motion conversion mechanism comprises a rotary motion part and a linear motion part which are matched with each other, the linear motion of the motion conversion mechanism corresponds to the rotary motion in proportion, the rotary motion part is detachably and fixedly connected with the motor, and the linear motion part is detachably and fixedly connected with the spool of the spool valve.

5. The electro-proportional hydraulic control system for a multiplex valve as defined in claim 4, wherein: the periphery of the motion conversion mechanism is provided with a sliding shell for limiting the linear motion part to rotate, two ends of the sliding shell are respectively connected with the motor and the servo hydraulic unit, the motion conversion mechanism is of a lead screw transmission structure, the rotary motion part is a ball screw, and the linear motion part is a ball nut.

6. The electro-proportional hydraulic control device for the multi-way valve as claimed in any one of claims 1 to 5, wherein: the servo control unit comprises a control input interface module and a sensor input module for receiving control signals, a motor driving module for controlling the operation of the motor and a central processor module for processing the control signals.

7. The electro-proportional hydraulic control system for a multiplex valve as defined in claim 6, wherein: the control input interface module of servo control unit possesses one or several kinds in communication protocol interface, switching value input interface, PWM input interface, the analog input interface, and servo control unit's output is the drive control of motor, includes: the control system comprises the motor, and is characterized by comprising the motor rotation speed control, position control, direction control, electrification stop control and power loss control.

8. The electro-proportional hydraulic control system for a multiplex valve as defined in claim 7, wherein: the control input interface of the servo control unit is used as the input of the electric proportional hydraulic control device, the piston rod of the servo hydraulic unit is used as the output of the electric proportional hydraulic control device, and the input and the output of the electric proportional hydraulic control device have the following corresponding relations:

(1) when the control signal input by the servo control unit is zero, the motor is powered off, the output of the servo hydraulic unit is in a floating state, and the main valve core of the multi-way valve returns to the middle position under the action of the main spring;

(2) when the control signal input by the servo control unit is not zero and does not change, the output state of the servo hydraulic unit is as follows: the main valve core of the multi-way valve is in a corresponding position deviated from the middle position when the main valve core of the multi-way valve stops moving after moving to a position corresponding to the control signal;

(3) when the control signal input by the servo control unit is not zero and changes, the output state of the servo hydraulic unit is as follows: the main valve core of the multi-way valve moves by a distance corresponding to the variable quantity of the control signal, and the main valve core of the multi-way valve moves forwards or backwards by a distance corresponding to the variable quantity of the input control signal from the current position.

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