CN212155303U - Electric proportional control hydraulic multi-way reversing valve - Google Patents
Electric proportional control hydraulic multi-way reversing valve Download PDFInfo
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- CN212155303U CN212155303U CN202020906455.0U CN202020906455U CN212155303U CN 212155303 U CN212155303 U CN 212155303U CN 202020906455 U CN202020906455 U CN 202020906455U CN 212155303 U CN212155303 U CN 212155303U
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Abstract
The utility model discloses an electricity proportional control hydraulic pressure multichannel switching-over valve, including the valve body that has a plurality of switching-over units, every switching-over unit all contains a main valve core, and a set of electricity proportional hydraulic control device is installed to main valve core's one end, and electricity proportional hydraulic control device drives the servo hydraulic unit of main valve core after being used for carrying out power amplification with the signal that drive unit provided including the drive unit that is used for converting motor rotary motion into linear motion. The utility model discloses a hydraulic pressure multichannel conversion valve main valve core can follow the action of piston valve barrel, and the action of motor is followed to the piston valve barrel, realizes can stopping in the stroke any position electrification, returns the meso position when losing the electricity. The utility model discloses an electricity proportional control hydraulic pressure multichannel conversion valve can solve current electricity proportional control multiple unit valve and realize with high costs, and control algorithm is complicated, the difficult problem of popularizing and applying by a large scale.
Description
Technical Field
The utility model belongs to the technical field of the electric liquid servo control of hydraulic pressure multichannel switching-over valve, mainly relate to centralized control's among the hydraulic system proportional multi-way switching-over valve, concretely relates to electric proportional control hydraulic pressure multichannel switching-over valve.
Background
The multi-way reversing valve (multi-way valve for short) is a control valve group widely applied to a mobile mechanical hydraulic system, and controls the reversing of a hydraulic actuating element (such as a hydraulic cylinder) to enable hydraulic oil in the hydraulic system to control the movement direction and speed of the actuating element; the hydraulic control system can combine various valves according to the requirements of different hydraulic systems, has the advantages of compact structure, simple pipeline, small pressure loss, large flow and convenient installation, and is widely applied to engineering machinery, hoisting and transporting machinery and other walking machinery requiring to operate a plurality of executing elements to move.
The proportional multi-way reversing valve is a direction and flow composite control valve which is formed by adding a proportional function on the basis of the traditional multi-way reversing valve. At present, the control modes of a 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 by changing the angle of a handle, the pilot type directly drives the main valve core to move after the pilot valve core is driven to move by driving a pilot valve core to convert into hydraulic pressure, and the pilot valve can be controlled directly by the handle or by an electric signal control electromechanical conversion mechanism. 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. However, the scheme has high implementation cost and complex control algorithm and is 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 proportional control hydraulic pressure multichannel switching-over valve for solve current electricity proportional control multichannel 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:
the electric proportional control hydraulic multi-way reversing valve comprises a valve body with a plurality of reversing units, each reversing unit comprises a main valve core, one end of each main valve core is provided with a group of electric proportional hydraulic control devices, the other end of each main valve core can be selectively assembled with a manual control device, each electric proportional hydraulic control device comprises a driving unit and a servo hydraulic unit, the driving unit is used for converting the rotary motion of a motor into linear motion, and the servo hydraulic unit is used for amplifying the power of signals provided by the driving unit and then driving the main valve cores.
Optionally, 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 is slidably connected in the piston valve sleeve and forms a four-way slide valve with the piston valve sleeve, the piston valve sleeve is used as a piston of the servo hydraulic unit and also used as a valve sleeve of the four-way slide valve, the piston valve sleeve is slidably connected in the servo cylinder body 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 comprises a slide valve core and a slide valve centering reset device, one end of the slide valve core is detachably and fixedly connected with the control rod, and one end of the piston valve sleeve, which;
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, the control oil port a3 is communicated with a hydraulic cylinder control rod cavity through an oil duct, the control oil port b3 is communicated with the hydraulic cylinder piston rod cavity, and when the slide valve core reciprocates in the piston valve sleeve, 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 slide valve core and the piston valve sleeve.
Optionally, the spool and the piston valve housing of the spool valve are in a spool valve type five-position four-way reversing valve structure, and five positions of the spool 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, that is:
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.
Optionally, five undercut grooves for communicating oil are formed in the piston valve sleeve, 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 valve of the spool valve is provided with three shoulders for opening or closing the oil ports, and when the spool valve of the spool valve reciprocates in the piston valve sleeve, the undercut grooves are opened or closed through the shoulders on the spool valve of the spool valve, so that the oil ports communicated with the undercut grooves are connected 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.
Optionally, a pilot oil inlet P1 and a pilot oil return port T1 are formed in the servo cylinder, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are formed between the piston valve sleeve and the servo cylinder in the axial direction, the oil inlet groove P2 and the oil return groove T2 may be formed in the outer periphery of the piston valve sleeve or in the inner wall of the servo cylinder, the oil inlet P3 of the piston valve sleeve is communicated with the pilot oil inlet P1 through the oil inlet groove P2, the oil return port T3 of the piston valve sleeve is communicated with the pilot oil return port T1 through the oil return groove T2, the piston valve sleeve is moved in the servo cylinder, the oil inlet groove P2 is communicated with the pilot oil inlet P1 all the time, and the oil return groove T2 is communicated.
Optionally, the spring restoring force F of the spool return spring in the spool centering return device is:
wherein, TmTorque required for rotation of the drive unit in the event of loss of power, TnWhen the driving unit is in screw transmission, s is the nut lead and eta is the transmission efficiency.
Optionally, the stiffness of the spool return spring in the spool centering return device is less than the stiffness of the main spool return spring. When the motor is in power failure, the piston valve sleeve of the servo hydraulic unit is in a floating state under the action of the slide valve return spring, and the action of the manual control device of the main valve core is not influenced.
Optionally, the driving unit includes a motor and a motion conversion mechanism, the motor employs a micro motor to reduce the installation size, the motor is connected with a motor control module, and can be integrated with the motor as a whole, the motor control module is the conventional technology in the prior art, and details are not repeated in detail, the motion conversion mechanism can be a screw transmission structure, a rack and pinion transmission, a worm and gear transmission and the like, and can convert a rotary motion into a linear motion, the motion conversion mechanism includes 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 can be detachably and fixedly connected with the motor, and the linear motion piece can be detachably and fixedly connected with.
Adopt above-mentioned technical scheme, the utility model has the advantages of it is following:
1. it is with low costs, compare among the prior art and utilize pilot valve, proportion electro-magnet and sensing element LVDT displacement sensor to carry out electric proportional control's method to multichannel switching-over valve, the technical scheme of the utility model utilize the rotary motion conversion of drive unit with the motor to linear reciprocating motion, utilize servo hydraulic unit as helping hand drive multichannel switching-over valve main valve core, wherein, servo hydraulic unit's servo principle is: the multi-position four-way slide valve has the advantages that the piston valve sleeve and the slide valve core of the multi-position four-way slide valve are designed on the basis of the piston in the servo cylinder body, the piston valve sleeve is used as a feedback mechanism, meanwhile, the slide valve centering reset device is arranged in the piston valve sleeve and controls the motion of the slide valve core together with the driving unit, so that the piston valve sleeve in the servo hydraulic unit can accurately follow the motion of the slide valve core, and then the main valve core of the multi-way reversing valve is driven by a transmission part, and the electric proportional control of the multi-way reversing valve is. The utility model discloses electricity proportional control's realization need not expensive high-speed valve or proportional valve to and LVDT sensor, cost greatly reduced.
2. Control accuracy is high, the technical scheme of the utility model the moving speed that can decide main valve element according to the rotational speed of motor is fast slow, according to the position of the rotatory angle decision main valve element of motor, servo hydraulic unit follows drive unit's removal completely, main valve element's removal displacement relies on the helical pitch of lead screw or the machining precision decision of pitch, the control accuracy who makes multichannel switching-over valve is high, and simultaneously, the mechanical transmission simple structure that this drive unit adopted, control method is simple, the reaction is quick, reliable, low cost. If direct electric proportional control who adopts motor drive screw nut to realize multichannel switching-over valve, because the size of most multichannel switching-over valves each antithetical couplet is less relatively in the width direction, the power undersize of optional motor, be not enough to drive the main valve core, the utility model discloses a method of the little miniature motor drive servo hydraulic unit of size, the servo hydraulic unit is amplified and is converted into hydraulic signal back drive multichannel switching-over valve main valve core with drive unit's displacement and speed signal by servo hydraulic unit, solves the electric proportional control problem of multichannel switching-over valve.
3. Response speed is fast the utility model discloses an electricity proportional control hydraulic pressure multichannel switching-over valve control in-process, servo hydraulic unit is following closely the action of motor and moves, and after the motor stall, servo hydraulic unit also stops the oil feed oil return, and after the motor loses the electricity, servo hydraulic unit gets back to the meso-position immediately under main valve element reset spring's effect, has the fast advantage of response speed.
4. Compatibility is better, as long as satisfy the condition that the motor loses the electricity, the action of multichannel reversing valve main valve core is decided by manual control device completely, consequently the utility model provides an electricity proportion hydraulic control device and manual control device possess good compatibility.
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 perspective view of the present invention;
FIG. 2 is an exploded view of the drive unit of FIG. 1;
FIG. 3 is a schematic cross-sectional view of FIG. 2;
FIG. 4 is an exploded view of the servo hydraulic unit of FIG. 1;
FIG. 5 is a perspective view of the piston valve sleeve of FIG. 4;
FIG. 6 is one of the schematic cross-sectional structural views of FIG. 4;
FIG. 7 is a second schematic cross-sectional view of FIG. 4;
FIG. 8 is a schematic view of the forward servo control of the motor of the present invention;
fig. 9 is a schematic view of the motor stop servo control of the present invention;
fig. 10 is a schematic diagram of the motor reverse servo control of the present invention;
fig. 11 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;
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 flange connection; 492. a valve core connecting portion; 493. a position avoiding part.
Detailed Description
In order to make the technical purpose, technical solution and advantageous effects of the present invention clearer, the following description of the technical solution of the present invention is made with reference to fig. 1 to 11 and the following embodiments, wherein 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.
An embodiment of an electric proportional control hydraulic multi-way directional valve:
an electric proportional control hydraulic multi-way reversing valve comprises a valve body 11 with a plurality of reversing units, each reversing unit comprises a main valve core 12, one end of each main valve core 12 is provided with a group of electric proportional hydraulic control devices, the other end of each main valve core 12 can be selectively assembled with a manual control device 2, and each reversing unit can replace the manual control device by the electric proportional hydraulic control device. The electro-proportional hydraulic control device comprises a driving unit 3 for converting the rotary motion of a motor into linear motion and a servo hydraulic unit 4 for amplifying the power of signals (such as displacement, speed, electrification stop, power loss and the like) provided by the driving unit 3 and then driving a main valve element 12.
Further, as shown in fig. 2 and 3, the driving unit 3 includes a motor 31 and a motion conversion mechanism, the motor 31 employs a micro motor 31 to reduce the installation size, the motor 31 is connected to a control module of the motor 31, and can be integrated with the motor 31, the control module of the motor 31 is a conventional technology in the prior art, details are not repeated, the motion conversion mechanism can be a transmission structure that converts a rotational motion into a linear motion, such as a screw transmission structure, a rack-and-pinion transmission, a worm-and-gear transmission, and the like, the motion conversion mechanism includes a rotational motion member and a linear motion member that are matched with each other, the linear motion of the motion conversion mechanism corresponds to the rotational motion in proportion, and the rotational motion member is detachably and fixedly connected with an output. 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 installs on motor mounting panel 37, motor 31 axle mounting groove has been seted up to ball 32's one end, the rotation axis tip of motor 31 inserts and is connected with ball 32 in the motor 31 axle mounting groove, 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. 4 to 7, the servo hydraulic unit 4 includes a servo cylinder 41, a piston valve sleeve 42, and a valve core assembly, the valve core assembly is slidably connected in the piston valve sleeve 42 and forms a four-way valve with the piston valve sleeve 42, the piston valve sleeve 42 is used as both a piston of the servo hydraulic unit and a valve sleeve of the four-way valve, and 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 cavity 411 and a cylinder piston rod cavity 412.
Specifically, fixedly connected with piston left end lid 45 can be dismantled to piston valve barrel 42's one end, fixedly connected with piston right end lid 46 can be dismantled to piston valve barrel 42's the other end, and piston left end lid 45 and piston right end lid 46 can be threaded connection respectively at piston valve barrel 42's both ends, and cylinder cover 47 before the servo cylinder of fixedly connected with can be dismantled to servo cylinder 41's one end, and cylinder cover 48 behind the servo cylinder of fixedly connected with can be dismantled to servo cylinder 41's the other end forms between piston left end lid 45 and the servo cylinder cover 47 the pneumatic cylinder control rod chamber 411, form between piston right end lid 46 and the servo cylinder cover 48 pneumatic cylinder piston rod chamber 412.
The spool assembly comprises a spool valve 43 and a spool valve centering and resetting device, one end of the spool valve 43 is detachably and fixedly connected with the linear motion part (i.e. the moving block 35) of the driving unit 3 through an operating rod 49, and one end of the piston valve sleeve 42 positioned in a piston rod cavity 412 of the hydraulic cylinder is detachably and fixedly connected with the main spool 12.
Specifically, the control lever 49 includes a flange connection portion 491 and a spool connection portion 492, the flange connection portion 491 is detachably and fixedly connected with the linear motion member of the driving unit 3, the spool connection portion 492 is detachably and fixedly connected with one end of the spool 43 of the spool valve, and a position avoiding portion 493 for avoiding interference with the linear motion member of the driving unit 3 is further provided on one side of the control lever 49 close to the driving unit 3. The linear motion member of the driving unit 3 can reciprocate in the clearance 493 without being affected, the flange connection portion 491 can be connected with the linear motion member of the driving unit 3 by a screw, the spool connection portion 492 can be connected with the spool 43 of the spool valve in a threaded manner, and the connection can also be in a pin connection manner (namely, pin holes are formed in the spool connection portion 492 and the spool 43 of the spool valve in the same direction, and the spool connection portion 492 and the spool 43 of the spool valve are connected into a whole by a positioning pin shaft inserted into the two pin holes at the same time), and the connection manner occupies a small space and can also be connected by a coupler, a flange and the like.
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 slide valve spool 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 slide valve spool 43 and the piston valve sleeve 42.
Specifically, at least one control oil hole a2 is formed in 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 formed in 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 slide valve centering and resetting device can be installed at any one end or two ends of the slide valve spool 43, in this embodiment, the slide valve centering and resetting device is installed at one end of the slide valve spool 43 close to the driving unit 3, specifically, a stepped hole is formed in the piston left end cover 45, one end of the control rod 49 is slidably connected in the stepped hole, the stepped hole comprises a fine hole section and a coarse hole section, the slide valve centering and resetting device is installed at the coarse hole section of the stepped hole, the slide valve centering and resetting device comprises a slide valve resetting spring 441 and two spring seats 442, the two spring seats 442 are slidably connected in the coarse hole section, in a natural state of the slide valve resetting spring 441, the end surface of one spring seat 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 slide valve spool 43, and the distance.
When the operating rod 49 has motion input, the position of the spool valve 43 is determined by the operating rod 49, when the operating 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 reset device, that is, when the spool valve 43 moves rightwards under the driving of the operating rod 49, the operating rod 49 pushes the left spring seat 442 to move rightwards, the spool valve reset spring 441 is compressed, and when the operating rod 49 has no motion input (the motor is de-energized), the spool valve 43 moves leftwards to return to the neutral position under the action of the spool valve reset spring 441; that is, when the spool valve 43 moves leftward by the operation rod 49, the land on the spool valve 43 pushes the right spring seat 442 leftward, the spool return spring 441 is compressed, and when the operation rod 49 has no motion input (the motor is de-energized), the spool valve 43 moves rightward by the spool return spring 441 to return to the neutral position.
Specifically, a spool accommodating groove 461 is formed in one side of the piston right end cover 46 close to the spool 43 of the spool valve, the length of the spool accommodating groove 461 is greater than the maximum stroke of the spool 43 of the spool valve, a piston rod 462 is arranged on one side of the piston right end cover 46 far away from the spool 43 of the spool valve, and the piston valve sleeve 42 is detachably and fixedly connected with the main spool 12 through the piston rod 462; specifically, one end of the piston rod 462 is provided with a pin hole, and the piston rod 462 passes through the servo cylinder rear cylinder cover 48 and is connected with the main valve element 12 of the multi-way valve reversing unit through a pin shaft.
Four regions are arranged between the piston valve sleeve 42 and the servo cylinder 41 in the servo hydraulic unit 4, namely a circumferential isolation region at two ends, an anti-rotation groove region, two oil groove regions which are not communicated with each other and an axial isolation region which separates the two oil groove regions, 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 larger than the stroke of the piston valve sleeve 42, so that in the moving process of the piston valve sleeve 42 in the servo cylinder 41, the oil inlet groove is always communicated with an oil inlet oil way, and the oil return groove is always communicated with an oil return way.
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, the spool valve 43 and the piston valve housing 42 are in a spool valve type five-position four-way reversing valve structure, and five positions of the spool 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, that is:
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.
Furthermore, 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 valve 43 of the spool valve, so that the oil ports communicated with the undercut grooves are switched on 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.
Further, a pilot oil inlet P1 and a pilot oil return port T1 are formed in the servo cylinder 41, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are formed between the piston valve sleeve 42 and the servo cylinder 41 along the axial direction, the oil inlet groove P2 and the oil return groove T2 can be formed on the periphery of the piston valve sleeve 42 or on the inner wall of the servo cylinder 41, an oil inlet P3 of the piston valve sleeve 42 is communicated with the pilot oil inlet P1 through the oil inlet groove P2, an oil return port T3 of the piston valve sleeve 42 is communicated with the pilot oil return port T1 through the oil return groove T2, the oil inlet groove P2 is communicated with the pilot oil inlet P1 all the time, and the oil return groove T2 is communicated with the pilot oil return port T1 all the time during the movement of.
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.
Specifically, a valve sleeve hole coaxial with the spool valve 43 of the spool valve is formed in the piston valve sleeve 42, a shoulder is in clearance fit with the valve sleeve hole, the position of the drive unit 3 is left, the shoulder on the spool valve 43 is sequentially marked as a first shoulder, a second shoulder and a third shoulder from left to right, undercut grooves in the valve sleeve hole are sequentially marked as a first undercut groove, a second undercut groove, a third undercut groove, a fourth undercut groove and a fifth undercut groove from left to right, the first undercut groove, the second undercut groove, the third undercut groove, the fourth undercut groove and the fifth undercut groove respectively correspond to the left oil return port T3, the control oil port a3, the oil inlet P3, the control oil port b3 and the right oil return port T3, the width of the second shoulder is greater than that of the third undercut groove, the widths of the first shoulder and the second shoulder are greater than those of the first undercut groove and the fifth undercut groove, and the left and right oil return ports T3 are respectively communicated with.
Further, the spring restoring force F of the spool valve restoring spring 441 in the spool valve centering and restoring device is as follows:
wherein, TmTorque, T, required for rotation of the drive unit 3 when de-energizednWhen the driving unit 3 is in power-on, the torque is the rotating torque, s is the moving distance of the linear moving part when the rotating moving part rotates for a circle, and when the driving unit 3 is in lead screw transmission, s is the nut lead and eta is the transmission efficiency.
In the event of a loss of power to the drive unit 3, the minimum spring restoring force F of the slide valve return spring 441minCan push the slide valve core 43 and the linear motion part to move towards the middle position, and simultaneously overcome the friction force in the transmission process and rotate the rotary motion part when the driving unit 3 is powered offRequired torque Tm，
When the driving unit 3 is powered, the slide valve return spring 441 can drive the rotary motion member to rotate while overcoming the friction force during the transmission and the maximum spring restoring force F of the slide valve return spring 441max，
Further, the stiffness of the spool return spring 441 in the spool centering return device is less than the stiffness 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 spool valve return spring 441, and the action of the manual control device 2 of the main spool 12 is not influenced.
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. 8, when the motor 31 rotates forward, the motor 31 drives the spool valve 43 to move continuously, and 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, so that the oil is continuously fed into the piston rod cavity 412 of the hydraulic cylinder, the piston valve sleeve 42 is pushed to continuously close the opening degree of the spool valve 43, and the main valve core of the multi-way reversing valve can move leftward and open the main valve right reversing position of the multi-way reversing valve.
As shown in fig. 9, when the motor 31 stops rotating with electricity, because the spool 43 is in the right direction-changing position immediately after stopping, the cylinder piston rod chamber 412 still does not receive oil, the spool 43 stops moving, the piston valve sleeve 42 continues moving, the oil inlet P3 is closed, oil is stopped, the oil return port T3 on the right side of the spool 43 is in the closed state, at this time, the spool 43 is in the right stop position, the cylinder piston rod chamber 412 is closed, the multi-way spool formed by the spool and the piston valve sleeve cannot return to the neutral position, and the main spool 12 of the multi-way spool is in a certain opening position of the right stop position.
As shown in fig. 10, when the motor 31 stops from being charged and starts to rotate reversely, 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 is continuously in the stop state, but the oil return port T3 is opened and enters the middle position, both the cylinder lever chamber 411 and the cylinder rod chamber 412 are communicated with the oil return port T3, at this time, the piston rod 462 pushes the piston valve sleeve 42 to retreat, i.e., the piston valve sleeve 42 follows the spool 43 to move rightward under the external force, e.g., the main spool return spring 22 of the multi-way valve main valve, so as to continuously close the opening degree of the oil return port T3.
When the motor 31 stops rotating reversely, the spool valve 43 of the slide valve stops moving, the piston valve sleeve 42 continues moving to close the opening of the right oil return port T3, the spool valve 43 of the slide valve 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. 11, after the motor 31 is de-energized at any position, 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 to rotate under the action of the external force when the motor 31 is de-energized), the motor 31 is de-energized and rotates reversely, the spool valve 43 returns to the neutral position, at this time, the cylinder lever cavity 411 and the cylinder rod cavity 412 are respectively communicated with the oil return port T3, the piston valve sleeve 42 is in a floating state, the multi-way valve main valve spool 12 returns to the neutral position under the action of the restoring force of the multi-way valve main valve spool return spring 22, the piston valve sleeve 42 of the servo hydraulic unit 4 returns to the neutral position.
On the contrary, when the motor 31 starts to be electrified for reverse rotation, the basic principle and the control process are the same as those when the motor 31 is electrified for forward rotation, the main valve core of the multi-way reversing valve can be moved rightwards, and the main valve of the multi-way reversing valve is opened for left reversing; 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 electric proportional control hydraulic multiple directional control valve, comprising a valve body having a plurality of directional control units, each directional control unit comprising a main spool, characterized in that: one end of each main valve core is provided with a group of electric proportional hydraulic control devices, and each electric proportional hydraulic control device comprises a driving unit for converting the rotary motion of a motor into linear motion and a servo hydraulic unit for amplifying the power of a signal provided by the driving unit and then driving the main valve core.
2. The electro-proportional control hydraulic multi-way directional valve of 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 is connected in the piston valve sleeve in a sliding mode and forms a four-way slide valve 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 comprises a slide valve core and a slide valve centering reset device, one end of the slide valve core is detachably and fixedly connected with the control rod, and one end, located in the hydraulic cylinder piston rod cavity, of the;
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, the control oil port a3 is communicated with a hydraulic cylinder control rod cavity through an oil duct, the control oil port b3 is communicated with the hydraulic cylinder piston rod cavity, and when the slide valve core reciprocates in the piston valve sleeve, 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 slide valve core and the piston valve sleeve.
3. The electro-proportional control hydraulic multi-way directional valve of claim 2, wherein: the slide valve spool and the piston valve pocket are of a slide valve type five-position four-way reversing valve structure, and 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, namely:
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.
4. The electro-proportional control hydraulic multi-way directional valve of claim 3, wherein: five undercut grooves for communicating oil are formed in the piston valve sleeve, an oil inlet P3, an oil return port T3, a control oil port a3 and a control oil port b3 are respectively formed in different undercut grooves, the slide valve spool is provided with three shoulders for opening or closing the oil ports, 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 in 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 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 side.
5. The electro-proportional control hydraulic multi-way directional valve of claim 2, wherein: the servo cylinder body is provided with a pilot oil inlet P1 and a pilot oil return port T1, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are axially formed between the piston valve sleeve and the servo cylinder body, the oil inlet P3 of the piston valve sleeve is communicated with the pilot oil inlet P1 through the oil inlet groove P2, the oil return port T3 of the piston valve sleeve is communicated with the pilot oil return port T1 through the oil return groove T2, the piston valve sleeve is moved in the servo cylinder body, 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.
6. The electro-proportional control hydraulic multi-way directional valve of claim 2, wherein: the spring restoring force F of the slide valve restoring spring in the slide valve centering and restoring device is as follows:
wherein, TmTorque required for rotation of the drive unit in the event of loss of power, TnWhen the driving unit is powered on, the rotating torque is the rotating torque, s is the moving distance of the linear moving part when the rotary moving part rotates for a circle, and eta is the transmission efficiency.
7. The electro-proportional control hydraulic multi-way directional valve of claim 2, wherein: the rigidity of a slide valve reset spring in the slide valve centering reset device is smaller than that of a main valve core reset spring.
8. An electrically proportional controlled hydraulic multiple directional control valve according to any of claims 2 to 7, 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.
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| CN202020906455.0U CN212155303U (en) | 2020-05-26 | 2020-05-26 | Electric proportional control hydraulic multi-way reversing valve |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112524295A (en) * | 2020-12-09 | 2021-03-19 | 江苏天域阀业制造有限公司 | Multi-way angle valve for PTA, polyolefin and residual oil hydrogenation industry |
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2020
- 2020-05-26 CN CN202020906455.0U patent/CN212155303U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112524295A (en) * | 2020-12-09 | 2021-03-19 | 江苏天域阀业制造有限公司 | Multi-way angle valve for PTA, polyolefin and residual oil hydrogenation industry |
| CN112524295B (en) * | 2020-12-09 | 2022-04-05 | 江苏天域阀业制造有限公司 | Multi-way angle valve |
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