CN211715438U

CN211715438U - Electro-hydraulic control valve capable of regulating flow gain

Info

Publication number: CN211715438U
Application number: CN202020029634.0U
Authority: CN
Inventors: 刘丽; 陆倩倩; 丁川
Original assignee: Zhejiang University City College ZUCC
Current assignee: Zhejiang University City College ZUCC
Priority date: 2020-01-07
Filing date: 2020-01-07
Publication date: 2020-10-20
Anticipated expiration: 2030-01-07

Abstract

The utility model discloses an electrohydraulic control valve capable of regulating flow gain, which comprises an upper valve body, a lower valve body, an upper pressure compensation plate, a lower pressure compensation plate, a valve core, an oil inlet channel, an oil outlet channel and an oil return channel, wherein a first guide constraint mechanism for driving the valve core to move along the left-right direction and a second guide constraint mechanism for driving the valve core to move along the front-back direction are respectively arranged around the valve core; when the first guide constraint mechanism and the second guide constraint mechanism push the valve core to do compound motion in two freedom degrees, the opening area gradient of the valve port of the valve core can be continuously changed, so that the flow gain is changed, and the control on the flow gain of the control valve is realized. The utility model provides a flow gain of the electro-hydraulic control valve among the prior art by self mechanical structure injects or flow gain control system is bulky and control complicated technical problem, realized very big improvement electro-hydraulic control system's dynamic performance's beneficial effect.

Description

Electro-hydraulic control valve capable of regulating flow gain

Technical Field

The application belongs to the field of fluid transmission and control, and particularly relates to an electro-hydraulic control valve capable of regulating and controlling flow gain.

Background

In recent years, industrial technology is rapidly developed, an electro-hydraulic control system is widely applied to various fields of industrial manufacturing, ships, metallurgy and engineering machinery, a hydraulic valve is used as a core element of the electro-hydraulic control system, and the flow characteristic, stability and reliability of the hydraulic valve directly determine the quality of the whole system. With the increasing variety and application occasions of hydraulic equipment, various working condition action characteristics are often required in the working process, so that higher and higher requirements are provided for the output performance of the electro-hydraulic control system. From the transfer function of a general electro-hydraulic control system, it can be found that the magnitude of the flow gain of an electro-hydraulic control valve (an electro-hydraulic proportional or servo valve) can directly influence the open-loop gain of the system, so that the control performance of the system is directly influenced.

At present, there are two main ways to change the flow gain: the first mode is that the area gradient of the valve port changes with the opening degree of the valve port; in the second mode, multi-valve parallel control is adopted. The first method is to provide a semicircular, V-shaped, inverted V-shaped, trapezoidal or other combined throttling notch on the valve core or the valve sleeve, so that when the valve core moves on one degree of freedom, the minimum flow area of the valve port changes along with the change of the area gradient. However, this method is limited by the mechanical structure of the valve core or the valve sleeve after the valve is machined, and it is impossible to realize controllable and adjustable flow gain in engineering applications. The second mode needs multiple groups of electro-hydraulic control valves (electro-hydraulic proportion or servo valves) to cooperatively control the same execution element, each valve is independently controlled, multi-stage adjustment is realized, the requirement of flow gain switching change can be met, but the volume of the combined valve is large, and a control system is complex.

Therefore, the above-mentioned prior art electrohydraulic control valve has at least the following technical problems: the flow gain is limited by the self mechanical structure or the flow gain control system is bulky and complex to control.

SUMMERY OF THE UTILITY MODEL

The embodiment of the application provides an electro-hydraulic control valve capable of regulating and controlling flow gain, and the electro-hydraulic control valve is used for solving the technical problems that the flow gain of the electro-hydraulic control valve in the prior art is limited by a self mechanical structure or a flow gain control system is large in size and complex in control. In the embodiment of the application, the upper pressure compensation plate, the valve core and the lower pressure compensation plate which are stacked up and down are buckled to form the oil inlet channel, the oil outlet channel and the oil return channel, and when the valve core deviates on a horizontal plane, the area gradient of a valve port for communicating the oil inlet channel and the oil outlet channel can be changed; the first guide constraint mechanism driving the valve core to move left and right and the second guide constraint mechanism driving the valve core to move front and back are arranged to push the valve core to do compound motion in two freedom directions, and the opening area gradient of the valve port of the valve core is continuously changed, so that the flow gain is changed, and the regulation and control of the flow gain of the control valve are realized. Because the first guide constraint mechanism and the second guide constraint mechanism of the embodiment of the application control and adjust the originally fixed flow gain of the control valve on the basis of normal flow or pressure control of a single control valve, the flow gain of the control valve is not limited by the mechanical structure of the control valve, meanwhile, the control mechanism has a simple structure and a small size, and the beneficial effect of greatly improving the dynamic performance of an electro-hydraulic control system is realized.

In order to solve the above problems, an embodiment of the present application provides an electrohydraulic control valve capable of regulating and controlling flow gain, where the hydraulic valve includes an upper valve body and a lower valve body that are fixedly connected with each other from top to bottom, a groove is formed in a lower surface of the upper valve body, and an upper pressure compensation plate and a lower pressure compensation plate that can only move up and down are sequentially arranged in the groove from top to bottom;

a valve core is arranged between the upper pressure compensation plate and the lower pressure compensation plate, and a first guide constraint mechanism for driving the valve core to move along the left-right direction and a second guide constraint mechanism for driving the valve core to move along the front-back direction are respectively arranged on the periphery of the valve core;

the first guide constraint mechanism comprises a first electro-mechanical converter and a first constraint device which are oppositely arranged along the left-right direction, and the first electro-mechanical converter is positioned outside the upper valve body and fixed on the left side surface of the upper valve body; the first electro-mechanical converter is provided with a first driving rod which horizontally extends rightwards and penetrates into the groove, and the first driving rod is abutted against the left side surface of the valve core so as to drive the valve core to move along the left-right direction; the first restraint device comprises a first baffle and a first spring push rod, the first baffle is fixed on the right side surface of the upper valve body, the first spring push rod horizontally penetrates through the first baffle along the left-right direction, the right end of the first spring push rod is in threaded connection with the first baffle, the left end of the first spring push rod extends into the groove and is connected with a first spring pressure head through a first spring, the first spring can stretch along the left-right direction, the first spring pressure head is connected with a first pressure ball, and the first pressure ball is abutted against the right side surface of the valve core;

the second guide constraint mechanism comprises a second electric-mechanical converter and a second constraint device which are oppositely arranged along the front-back direction, and the second electric-mechanical converter is positioned outside the upper valve body and fixed on the front side surface of the upper valve body; the second electro-mechanical converter is provided with a second driving rod which horizontally penetrates into the groove, and the second driving rod is abutted against the front side surface of the valve core so as to drive the valve core to move along the front-back direction; the second restraint device comprises a second baffle and a second spring push rod, the second baffle is fixed on the rear side face of the upper valve body, the second spring push rod horizontally penetrates through the second baffle along the front-rear direction, the rear end of the second spring push rod is in threaded connection with the second baffle, the front end of the second spring push rod extends into the groove and is connected with a second spring pressure head through a second spring, the second spring can stretch along the front-rear direction, the second spring pressure head is connected with a second pressure ball, and the second pressure ball is abutted against the right side face of the valve core;

an upper oil inlet groove, an upper oil outlet groove and an upper low pressure groove are respectively arranged on the lower surface of the upper pressure compensation plate;

the upper surface of the lower pressure compensation plate is respectively provided with a first lower oil inlet groove, a first lower oil outlet groove and a first lower low pressure groove; a second lower oil inlet groove, a second lower oil outlet groove and a second lower low pressure groove are respectively arranged on the lower surface of the lower pressure compensation plate, wherein the second lower oil inlet groove and the first lower oil inlet groove are symmetrically arranged about the central cross section of the lower pressure compensation plate, the second lower oil outlet groove and the first lower oil outlet groove are symmetrically arranged about the central cross section of the lower pressure compensation plate, and the second lower low pressure groove and the first lower low pressure groove are symmetrically arranged about the central cross section of the lower pressure compensation plate; the second lower oil inlet groove is communicated with the first lower oil inlet groove through a lower oil inlet hole, the second lower oil outlet groove is communicated with the first lower oil outlet groove through a lower oil outlet hole, and the second lower low-pressure groove is communicated with the first lower low-pressure groove through a lower low-pressure hole; the valve core is respectively provided with a middle oil inlet groove, a middle oil outlet groove and middle and low pressure holes which are vertically communicated, the right side of the middle oil outlet groove, the left side of the upper oil inlet groove and the left side of the first lower oil inlet groove form a valve port, the projection of the right side of the middle oil outlet groove on the valve core is a valve port curve, and the valve port curve is a curve or a broken line;

the first lower oil inlet groove and the upper oil inlet groove are arranged in an up-down symmetrical mode, the first lower oil outlet groove and the upper oil outlet groove are arranged in an up-down symmetrical mode, and the first lower low-pressure groove and the upper low-pressure groove are arranged in an up-down symmetrical mode; the middle oil outlet groove and the middle oil inlet groove are arranged at left and right intervals, and the length of the middle oil outlet groove along the left and right direction is greater than the distance between the first lower oil outlet groove and the first lower oil inlet groove;

an oil inlet, an oil outlet and an oil return port are arranged on the lower surface of the lower valve body, an oil inlet flow passage, an oil outlet flow passage and a low-pressure flow passage are respectively arranged in the lower valve body, the second lower oil inlet groove is communicated with the oil inlet through the oil inlet flow passage, the second lower oil outlet groove is communicated with the oil outlet through the oil outlet flow passage, and the second lower low-pressure groove is communicated with the oil return port through the low-pressure flow passage;

the second lower oil inlet groove, the lower oil inlet hole, the first lower oil inlet groove, the middle oil inlet groove and the upper oil inlet groove are vertically aligned and communicated to form a high-pressure cavity; the second lower oil outlet groove, the lower oil outlet hole, the first lower oil outlet groove, the middle oil outlet groove and the upper oil outlet groove are vertically aligned and communicated to form a working cavity; the second lower low-pressure groove, the lower low-pressure through hole, the first lower low-pressure groove, the middle and low-pressure hole and the upper low-pressure groove are aligned and communicated up and down to form a low-pressure cavity; the high-pressure cavity is communicated with the oil inlet through the oil inlet flow passage to form an oil inlet channel; the working cavity is communicated with the oil outlet through the oil outlet flow passage to form an oil outlet channel; the low-pressure cavity is communicated with the oil return port through the low-pressure flow passage to form an oil return passage;

a plurality of upper low-pressure holes are arranged in the upper pressure compensation plate, the bottom end openings of the upper low-pressure holes extend into the upper low-pressure grooves and are communicated with the upper low-pressure grooves, and the top end openings of the upper low-pressure holes are positioned on the upper surface of the upper pressure compensation plate;

the control valve also comprises a pressure compensation device, the pressure compensation device comprises a first mounting groove and a second mounting groove which are arranged on the lower surface of the upper valve body, the first mounting groove and the upper surface of the upper pressure compensation plate enclose a first adjusting cavity, and the second mounting groove and the upper surface of the upper pressure compensation plate enclose a second adjusting cavity; a first adjusting piston only capable of moving up and down is arranged in the first adjusting cavity, a second adjusting piston only capable of moving up and down is arranged in the second adjusting cavity, a first sealing device is arranged between the inner wall surface of the first adjusting cavity and the outer peripheral surface of the first adjusting piston, and a second sealing device is arranged between the inner wall surface of the second adjusting cavity and the outer peripheral surface of the second adjusting piston;

the upper valve body is also provided with a first pressure adjusting hole for inputting high-pressure control oil above the first adjusting piston and a second pressure adjusting hole for inputting working pressure control oil above the second adjusting piston; the bottom end of the first pressure adjusting hole is communicated with the bottom of the first mounting groove, the top end of the first pressure adjusting hole is located on the upper surface of the valve body and is communicated with the oil outlet, the bottom end of the second pressure adjusting hole is communicated with the bottom of the second mounting groove, and the top end of the second pressure adjusting hole is located on the upper surface of the valve body and is communicated with the oil inlet.

Furthermore, the first lower oil outlet groove and the first lower oil inlet groove are both square grooves, the first lower oil outlet groove and the first lower oil inlet groove are arranged at intervals and are aligned left and right, and the first lower low-pressure groove is a first circular ring groove surrounding the first lower oil inlet groove and the first lower oil outlet groove;

the second lower oil outlet groove and the second lower oil inlet groove are both square grooves, the second lower oil outlet groove and the second lower oil inlet groove are arranged at intervals and are aligned left and right, and the second lower low-pressure groove is a second circular ring groove surrounding the second lower oil inlet groove and the second lower oil outlet groove;

go up the oil feeding groove with last oil groove be square groove, just go up the oil feeding groove with last oil groove interval set up and control and align, last low-pressure groove encircle go up the oil feeding groove with last oil groove around the circular annular of third.

Furthermore, the middle oil inlet groove is an elliptical groove or a rectangular groove.

Furthermore, the valve port curve comprises a first line segment, a second line segment and a third line segment which are connected in sequence, wherein the second line segment is positioned on the right side of the first line segment and the second line segment; a first break angle is formed between the first line segment and the second line segment, a second break angle is formed between the third line segment and the second line segment, and the first break angle and the second break angle are the same in size.

Furthermore, the middle oil outlet groove comprises a rectangular groove positioned on the left side and a trapezoidal groove positioned on the right side, and the right side of the rectangular groove is communicated with the left side of the trapezoidal groove; the projection of the rectangular groove on the upper end face of the valve core is rectangular, the projection of the trapezoidal groove on the upper end face of the valve core is trapezoidal, and the right side edge of the rectangle is collinear with the lower bottom edge of the trapezoid.

Further, well oil outlet groove form by the combination of the bar groove that a plurality of interval set up, the bar groove be parallel to each other, the bar groove extend from the left hand right side level, the left end in bar groove is mutually aligned, the length in bar groove is inequality.

Furthermore, a plurality of upper low-pressure holes are arranged on the upper pressure compensation plate at intervals, and the upper low-pressure holes are arranged in a circle around the upper low-pressure groove.

Furthermore, the projection area of the middle oil outlet groove on the lower end face of the valve core is larger than the projection area of the first lower oil outlet groove on the lower end face of the valve core; the projection area of the middle oil inlet groove on the lower end face of the valve core is smaller than that of the first lower oil inlet groove on the lower end face of the valve core.

Furthermore, a plurality of middle and low pressure holes are arranged on the valve core at intervals, each middle and low pressure hole is arranged in a circle along the valve core, and the middle and low pressure holes are communicated with the upper low pressure groove above and the first lower low pressure groove below.

Furthermore, the valve core is plate-shaped, and the front side, the rear side, the left side and the right side of the valve core are respectively provided with a vertical plane at equal angular intervals; the first driving rod and the second driving rod respectively abut against the vertical planes on the left side and the front side; the first pressure ball is in point contact with the vertical plane on the right side of the valve core, and the second pressure ball is in point contact with the vertical plane on the rear side of the valve core.

One or more technical solutions in the embodiments of the present application have at least one or more of the following technical effects:

1) in the embodiment of the application, the upper pressure compensation plate, the valve core and the lower pressure compensation plate which are stacked up and down are buckled to form the oil inlet channel, the oil outlet channel and the oil return channel, and when the valve core deviates on a horizontal plane, the area gradient of a valve port for communicating the oil inlet channel and the oil outlet channel can be changed; the first guide constraint mechanism driving the valve core to move left and right and the second guide constraint mechanism driving the valve core to move front and back are arranged to push the valve core to do compound motion in two freedom directions, and the opening area gradient of the valve port of the valve core is continuously changed, so that the flow gain is changed, and the regulation and control of the flow gain of the control valve are realized. Because the first guide constraint mechanism and the second guide constraint mechanism of the embodiment of the application control and adjust the originally fixed flow gain of the control valve on the basis of normal flow or pressure control of a single control valve, the flow gain of the control valve is not limited by the self mechanical structure any more, meanwhile, the control mechanism has a simple structure and small volume, the technical problem that the flow gain of an electro-hydraulic control valve is limited by the self mechanical structure or the control structure has huge volume in the prior art is solved, and the beneficial effect of greatly improving the dynamic performance of the electro-hydraulic control system is realized. And because the continuity of the valve port continuous curve flow regulation is better, the flow has no obvious transient impact in the switching process, and the upper and lower gaps of the valve core are reduced under the pressure compensation effect through the pressure compensation plate, thereby reducing the leakage and effectively improving the control precision of the control valve.

2) The upper pressure compensation plate and the lower pressure compensation plate are respectively arranged on the floating valve core, the pressure compensation device is arranged on the upper pressure compensation plate, the pressure compensation device is adjusted to enable the upper pressure compensation plate to move downwards and press the valve core, and gaps between the upper end surface and the lower end surface of the valve core and between the upper pressure compensation plate and the lower pressure compensation plate are reduced, so that the leakage amount of the gaps is reduced, and the flow control precision of the control valve can be effectively improved.

3) The clearance between the upper end surface and the lower end surface of the valve core and the clearance between the upper pressure compensation plate and the lower pressure compensation plate are reduced, and oil pollutants and particulate matters can be prevented from entering a working clearance, so that the valve core is not easily scratched, abraded and stuck by the pollutants.

4) The valve port curve can be made into a continuous type or a discrete type, the continuous valve port curve can realize the function of stepless regulation of flow gain, and the discrete valve port curve can realize the function of stepped regulation of flow gain.

The foregoing description is only an overview of the technical solutions of the present application, and the present application can be implemented according to the content of the description in order to make the technical means of the present application more clearly understood, and the following detailed description of the present application is given in order to make the above and other objects, features, and advantages of the present application more clearly understandable.

Drawings

Fig. 1 is a cross-sectional view of an electro-hydraulic control valve with adjustable flow gain according to an embodiment of the present invention;

fig. 2 is a schematic structural diagram of an electro-hydraulic control valve capable of adjusting and controlling flow gain according to an embodiment of the present invention;

FIG. 3 is a sectional view taken along line B-B of FIG. 2;

fig. 4 is an exploded view of a portion of an electro-hydraulic control valve with adjustable flow gain according to an embodiment of the present invention;

fig. 5 is a first schematic diagram illustrating pressure calculation of an electro-hydraulic control valve capable of adjusting and controlling flow gain according to an embodiment of the present invention;

fig. 6 is a schematic diagram illustrating a pressure calculation of an electro-hydraulic control valve capable of adjusting and controlling flow gain according to an embodiment of the present invention;

fig. 7 is a flow gain adjustment operation diagram of an electro-hydraulic control valve capable of adjusting and controlling flow gain according to an embodiment of the present invention;

fig. 8 is a schematic diagram of a discrete structure of a valve element of an electrohydraulic control valve capable of adjusting and controlling flow gain according to an embodiment of the present invention.

Description of reference numerals: the hydraulic control valve comprises a first electro-mechanical converter 1, an upper valve body 2, a lower pressure compensation plate 3, an upper pressure compensation plate 4, a first adjusting piston 5, a second adjusting piston 6, a valve core 7, a first pressure ball 8, a first spring pressure head 9, a first spring 10, a first spring push rod 11, a first baffle 12, a lower valve body 13, a second electro-mechanical converter 14, a second pressure ball 15, a second spring pressure head 16, a second spring 17, a second spring push rod 18, a second baffle 19, a first lower oil inlet groove P1, a middle oil inlet groove P2, an upper oil inlet groove P3, a lower oil inlet hole P4, a second lower oil inlet groove P5, a first lower oil outlet groove 1, a middle oil outlet groove a2, an upper oil outlet groove a3, a lower oil outlet hole a4, a second lower oil outlet groove a5, a first lower low pressure groove t1, a lower low pressure hole 2, an upper low pressure groove t3, an upper low pressure hole t4, a 85t 5, a low pressure hole t6, a low pressure groove P36, a, The oil return port T, the oil inlet flow passage P, the oil outlet flow passage a, the low-pressure flow passage T, the high-pressure cavity P1, the working cavity A1, the low-pressure cavity T1, the valve port curve L, the first line section L1, the second line section L2, the third line section L3 and the strip-shaped groove e.

Detailed Description

The embodiment of the application provides an electro-hydraulic control valve capable of regulating and controlling flow gain, and the electro-hydraulic control valve is used for solving the technical problems that the flow gain of the electro-hydraulic control valve in the prior art is limited by a self mechanical structure or a flow gain control system is large in size and complex in control.

In order to solve the technical problems, the technical scheme provided by the application has the following general idea: an upper pressure compensation plate, a valve core and a lower pressure compensation plate which are stacked up and down are buckled to form an oil inlet channel, an oil outlet channel and an oil return channel, and when the valve core deviates on a horizontal plane, the area gradient of a valve port for communicating the oil inlet channel and the oil outlet channel can be changed; the first guide constraint mechanism driving the valve core to move left and right and the second guide constraint mechanism driving the valve core to move front and back are arranged to push the valve core to do compound motion in two freedom directions, and the opening area gradient of the valve port of the valve core is continuously changed, so that the flow gain is changed, and the regulation and control of the flow gain of the control valve are realized. Because the first guide constraint mechanism and the second guide constraint mechanism of the embodiment of the application control and adjust the originally fixed flow gain of the control valve on the basis of normal flow or pressure control of a single control valve, the flow gain of the control valve is not limited by the self mechanical structure any more, meanwhile, the control mechanism has a simple structure and small volume, the technical problems that the flow gain of an electro-hydraulic control valve is limited by the self mechanical structure or the control system has large volume and complicated control in the prior art are solved, and the beneficial effect of greatly improving the dynamic performance of the electro-hydraulic control system is realized. And because the continuity of the valve port continuous curve flow regulation is better, the flow has no obvious transient impact in the switching process, and the upper and lower gaps of the valve core are reduced under the pressure compensation effect through the pressure compensation plate, thereby reducing the leakage and effectively improving the control precision of the control valve.

The technical solutions of the present application are described in detail below with reference to the drawings and specific embodiments, and it should be understood that the specific features in the embodiments and examples of the present application are detailed descriptions of the technical solutions of the present application, and are not limitations of the technical solutions of the present application, and the technical features in the embodiments and examples of the present application may be combined with each other without conflict.

Fig. 1 is the embodiment of the utility model provides an in the embodiment of the cross-sectional view of an electrohydraulic control valve of can regulating and control flow gain, fig. 2 is the embodiment of the utility model provides an in the embodiment of the structure schematic diagram of an electrohydraulic control valve of can regulating and control flow gain, fig. 3 is B-B to the cross-sectional view in fig. 2, fig. 4 is the embodiment of the utility model provides an in the embodiment of a partial structure explosion chart of an electrohydraulic control valve of can regulating and control flow gain, as shown in fig. 1, 2, 3, 4, the hydrovalve include upper valve body 2 and lower valve body 13 that upper and lower fixed link to each other, upper valve body 2's lower surface on be equipped with the recess, the recess in from top to bottom be equipped with in proper order all can only reciprocate last pressure compensating plate 4 and lower.

A valve core 7 is arranged between the upper pressure compensation plate 4 and the lower pressure compensation plate 3, and a first guide constraint mechanism for driving the valve core 7 to move along the left-right direction and a second guide constraint mechanism for driving the valve core 7 to move along the front-back direction are respectively arranged on the periphery of the valve core 7.

Specifically, the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are in clearance fit with the grooves, and the grooves are only internally provided with upper and lower gaps for the upper pressure compensation plate 4 and the lower pressure compensation plate 3 to move up and down, so that the upper pressure compensation plate 4 and the lower pressure compensation plate 3 can only move up and down. The upper pressure compensation plate 4, the lower pressure compensation plate 3 and the valve core 7 are all made of materials with high hardness, wear resistance, small friction coefficient and high surface smoothness, such as ceramics.

It should be noted that, in this embodiment, the upper direction when facing to fig. 1 is taken as the upper direction, the lower direction when facing to fig. 1 is taken as the lower direction, the left side when facing to fig. 1 is taken as the left direction, the right side when facing to fig. 1 is taken as the right direction, the side facing to the observer in fig. 1 is taken as the front, the side facing away from the observer in fig. 1 is taken as the rear, and the limitations of the upper, lower, left, right, front and rear directions are only for convenience of description and are not limitations of the technical solution of the present invention.

As shown in fig. 3, 4 and 7, the first guiding and constraining mechanism includes a first electromechanical transducer 1 and a first constraining device, which are oppositely disposed along the left-right direction, and the first electromechanical transducer 1 is located outside the upper valve body 2 and fixed on the left side surface of the upper valve body 2; the first electro-mechanical converter is provided with a first driving rod which horizontally extends rightwards and penetrates into the groove, and the first driving rod is abutted against the left side surface of the valve core so as to drive the valve core 7 to move along the left-right direction; first restraint ware include first baffle 12 and first spring push rod 11, first baffle 12 fix go up on the right flank of valve body 2, first spring push rod 11 along left right direction level run through first baffle 12, first spring push rod 11 the right-hand member with first baffle 12 threaded connection, first spring push rod 11 the left end extend to the recess in and be connected with first spring pressure head 9 through first spring 10, first spring 10 can stretch out and draw back along left right direction, first spring pressure head 9 be connected with first pressure ball 8, just first pressure ball 8 conflict be in on the right flank of case 7.

The second guiding constraint mechanism comprises a second electromechanical converter 14 and a second constraint device which are oppositely arranged along the front-back direction, and the second electromechanical converter 14 is positioned outside the upper valve body 2 and fixed on the front side surface of the upper valve body 2; the second electro-mechanical converter 14 is provided with a second driving rod horizontally penetrating into the groove, and the second driving rod is abutted against the front side surface of the valve core 7 so as to drive the valve core 7 to move along the front-back direction; the second restraint device comprises a second baffle plate 19 and a second spring push rod 18, the second baffle plate 19 is fixed on the rear side face of the upper valve body 2, the second spring push rod 18 horizontally penetrates through the second baffle plate 19 along the front-back direction, the rear end of the second spring push rod 18 is in threaded connection with the second baffle plate 19, the front end of the second spring push rod 18 extends into the groove and is connected with a second spring pressure head 16 through a second spring 17, the second spring 17 can stretch along the front-back direction, the second spring pressure head 16 is connected with a second pressure ball 15, and the second pressure ball 15 abuts against the right side face of the valve core 7.

Specifically, the valve core 7 is plate-shaped, a vertical plane is respectively arranged on the front side, the rear side, the left side and the right side of the valve core 7 (for example, the projection of the valve core 7 on the lower pressure compensation plate 3 is octagonal), and the first driving rod and the second driving rod respectively abut against the vertical plane on the left side and the front side; the first pressure ball 8 and the second pressure ball 15 are steel balls, the first pressure ball 8 is in point contact with the vertical plane on the right side of the upper valve core 7, and the second pressure ball 15 is in point contact with the vertical plane on the rear side of the valve core 7.

Specifically, the first spring push rod 11 and the first baffle 12 are converted into axial displacement of the first spring push rod 11 due to axial relative movement of threaded connection by rotating the first spring push rod 11, so that the pre-tightening force of the first spring 10 can be adjusted; similarly, the second spring push rod 18 is rotated to convert the axial relative movement between the second spring push rod 18 and the second baffle plate 19 due to the threaded connection into the axial displacement of the second spring push rod 18, so that the pre-tightening force of the second spring 17 can be adjusted.

As shown in fig. 4, the upper pressure compensation plate 4 is provided with an upper oil inlet groove p3, an upper oil outlet groove a3 and an upper low pressure groove t3 on the lower surface thereof.

As shown in fig. 5, the upper surface of the lower pressure compensation plate 3 is provided with a first lower oil inlet groove p1, a first lower oil outlet groove a1 and a first lower low pressure groove t 1; a second lower oil inlet groove p5, a second lower oil outlet groove a5 and a second lower low pressure groove t6 are respectively arranged on the lower surface of the lower pressure compensation plate 3, wherein the second lower oil inlet groove p5 and the first lower oil inlet groove p1 are symmetrically arranged about the central cross section of the lower pressure compensation plate 3, the second lower oil outlet groove a5 and the first lower oil outlet groove a1 are symmetrically arranged about the central cross section of the lower pressure compensation plate 3, and the second lower low pressure groove t6 and the first lower low pressure groove t1 are symmetrically arranged about the central cross section of the lower pressure compensation plate 3; and the second lower oil inlet groove p5 is communicated with the first lower oil inlet groove p1 through a lower oil inlet hole p4, the second lower oil outlet groove a5 is communicated with the first lower oil outlet groove a1 through a lower oil outlet hole a4, and the second lower low pressure groove t6 is communicated with the first lower low pressure groove t1 through a lower low pressure hole t 2.

Specifically, the central cross section refers to a cross section of the lower pressure compensation plate 3 located at the middle in the up-down direction.

As shown in fig. 4 and 6, the valve body 7 is provided with a middle oil inlet groove p2, a middle oil outlet groove a2 and a middle and low pressure hole t5 which are vertically penetrated, the right side of the middle oil outlet groove a2, the left side of the upper oil inlet groove p3 and the left side of the first lower oil inlet groove p1 form a valve port, the projection of the right side of the middle oil outlet groove a2 on the valve body 7 is a valve port curve L, and the valve port curve L is a curve or a broken line.

Specifically, when the right side of the middle oil outlet groove a2, the left side of the upper oil inlet groove p3 and the left side of the first lower oil inlet groove p1 are communicated up and down, the valve port is opened; when the right side of the middle oil outlet groove a2, the left side of the upper oil inlet groove p3 and the left side of the first lower oil inlet groove p1 are staggered, the valve port is closed. At this time, the spool 7 is in the home position. As shown in fig. 1 and 4, the first lower oil inlet groove p1 and the upper oil inlet groove p3 are vertically symmetrically arranged, the first lower oil outlet groove a1 and the upper oil outlet groove a3 are vertically symmetrically arranged, and the first lower low pressure groove t1 and the upper low pressure groove t3 are vertically symmetrically arranged; the middle oil outlet groove a2 and the middle oil inlet groove p2 are arranged at left and right intervals, and the length of the middle oil outlet groove a2 in the left and right direction is greater than the distance between the first lower oil outlet groove a1 and the first lower oil inlet groove p1 (since the first lower oil outlet groove a1 and the upper oil outlet groove a3 are symmetrically arranged and the first lower oil inlet groove p1 and the upper oil inlet groove p3 are symmetrically arranged, the length of the middle oil outlet groove a2 in the left and right direction is also necessarily greater than the distance between the upper oil outlet groove a3 and the upper oil inlet groove p 3); so that the middle oil outlet groove a2 can simultaneously communicate the oil inlet channel and the oil outlet channel when the valve core 7 is in the open state.

Specifically, the lower oil inlet groove p1 and the upper oil inlet groove p3 are disposed in an up-down symmetrical manner with respect to the plane where the valve element 7 is located, the lower oil outlet groove a1 and the upper oil outlet groove a3 are disposed in an up-down symmetrical manner with respect to the plane where the valve element 7 is located, and the first lower low pressure groove t1 and the upper low pressure groove t3 are disposed in an up-down symmetrical manner with respect to the plane where the valve element 7 is located.

As shown in fig. 1 and 3, an oil inlet P, an oil outlet a and an oil return port T are arranged on the lower surface of the lower valve body 13, an oil inlet flow passage P, an oil outlet flow passage a and a low-pressure flow passage T are respectively arranged in the lower valve body 13, the second lower oil inlet groove P5 is communicated with the oil inlet P through the oil inlet flow passage P, the second lower oil outlet groove a5 is communicated with the oil outlet a through the oil outlet flow passage a, and the second lower low-pressure groove T6 is communicated with the oil return port T through the low-pressure flow passage T.

The second lower oil inlet groove P5, the lower oil inlet hole P4, the first lower oil inlet groove P1, the middle oil inlet groove P2, the upper oil inlet grooves P3 and P5 are aligned up and down and penetrate through to form a high-pressure cavity P1; the second lower oil outlet groove a5, the lower oil outlet hole a4, the first lower oil outlet groove a1, the middle oil outlet groove a2, the upper oil outlet grooves a3 and a5 are aligned up and down and penetrate through to form a working chamber A1; the second lower low pressure groove T6, the lower low pressure hole T2, the first lower low pressure groove T1, the middle and low pressure hole T5 and the upper low pressure groove T3 are aligned and communicated with each other up and down to form a low pressure cavity T1; the high pressure cavity P1 is communicated with the oil inlet P through the oil inlet flow passage P to form an oil inlet channel; the working cavity A1 is communicated with the oil outlet A through the oil outlet flow passage a to form an oil outlet channel; the low-pressure cavity T1 is communicated with the oil return port T through the low-pressure flow passage T to form an oil return passage.

As shown in fig. 1 and 4, a plurality of upper low pressure holes t4 are formed in the upper pressure compensation plate 4, the bottom end openings of the upper low pressure holes t4 extend into the upper low pressure grooves t3 and are communicated with the upper low pressure grooves t3, and the top end openings of the upper low pressure holes t4 are located on the upper surface of the upper pressure compensation plate 4.

As shown in fig. 1 and 5, the control valve further includes a pressure compensation device, the pressure compensation device includes a first mounting groove and a second mounting groove which are formed on the lower surface of the upper valve body 2, the first mounting groove and the upper surface of the upper pressure compensation plate 4 enclose a first adjustment cavity, and the second mounting groove and the upper surface of the upper pressure compensation plate 4 enclose a second adjustment cavity; the first adjusting cavity is internally provided with a first adjusting piston 5 which can only move up and down, the second adjusting cavity is internally provided with a second adjusting piston 6 which can only move up and down, a first sealing device is arranged between the inner wall surface of the first adjusting cavity and the outer peripheral surface of the first adjusting piston 5, and a second sealing device is arranged between the inner wall surface of the second adjusting cavity and the outer peripheral surface of the second adjusting piston 6.

The upper valve body 2 is also provided with a first pressure adjusting hole for inputting high-pressure control oil above the first adjusting piston 5 and a second pressure adjusting hole for inputting working pressure control oil above the second adjusting piston 6; the bottom end of the first pressure adjusting hole is communicated with the bottom of the first mounting groove, the top end of the first pressure adjusting hole is located on the upper surface of the valve body 2 and is communicated with the oil outlet A, the bottom end of the second pressure adjusting hole is communicated with the bottom of the second mounting groove, and the top end of the second pressure adjusting hole is located on the upper surface of the valve body 2 and is communicated with the oil inlet P.

Specifically, when the first electro-mechanical converter 1 and the second electro-mechanical converter 14 are not operated, the valve spool 7 is in the original position, the valve port of the valve spool 7 is closed, and the high pressure chamber P1 is not communicated with the working chamber a1, that is, the oil inlet P is not communicated with the oil outlet a. The valve core 7 is in a suspension state under the action of oil films with equal pressure on the upper end surface and the lower end surface. The upper end surface and the lower end surface of the lower pressure compensation plate 3 are in a balanced suspension state under the action of oil films with the same pressure.

In the embodiment of the application, the upper pressure compensation plate 4, the valve core 7 and the lower pressure compensation plate 3 which are stacked up and down are buckled to form an oil inlet channel, an oil outlet channel and an oil return channel, and when the valve core 7 deviates on a horizontal plane, the area gradient of a valve port communicating the oil inlet channel and the oil outlet channel can be changed; the valve core 7 is pushed to do compound motion in two freedom degree directions by arranging a first guiding constraint mechanism capable of driving the valve core 7 to move left and right and a second guiding constraint mechanism capable of driving the valve core to move front and back, and the opening area gradient of the valve port of the valve core 7 is continuously changed, so that the flow gain is changed, and the flow gain of the control valve is regulated and controlled. Because the first guide constraint mechanism and the second guide constraint mechanism of the embodiment of the application control and adjust the originally fixed flow gain of the control valve on the basis of normal flow or pressure control of a single control valve, the flow gain of the control valve is not limited by the self mechanical structure any more, meanwhile, the control mechanism has a simple structure and small volume, the technical problems that the flow gain of an electro-hydraulic control valve is limited by the self mechanical structure or the control system has large volume and complicated control in the prior art are solved, and the beneficial effect of greatly improving the dynamic performance of the electro-hydraulic control system is realized.

In addition, because the continuity of the valve port continuous curve flow regulation is better, the flow has no obvious transient impact in the switching process, and the upper and lower gaps of the valve core are reduced under the pressure compensation effect through the pressure compensation plate, thereby reducing the leakage and effectively improving the control precision of the control valve.

Secondly, an upper pressure compensation plate 4 and a lower pressure compensation plate 3 are respectively arranged above and below the floating valve core 7, a pressure compensation device is arranged on the upper pressure compensation plate 4, the pressure compensation device is adjusted to enable the upper pressure compensation plate 4 to move downwards and press the valve core 7, and gaps between the upper end surface and the lower end surface of the valve core 7 and between the lower end surface of the upper pressure compensation plate 4 and the upper end surface of the lower pressure compensation plate 3 are reduced, so that the leakage amount passing through the gaps is reduced, and the flow control precision of the control valve can be effectively improved.

And finally, the gaps between the upper end surface and the lower end surface of the valve core 7 and the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are reduced, so that oil pollutants and particulate matters can be prevented from entering a working gap, and the valve core 7 is not easily scratched, abraded and stuck by the pollutants.

Specifically, when the control valve of the present invention is an electro-hydraulic proportional valve, the first electro-mechanical converter 1 and the second electro-mechanical converter 14 are both proportional electro-mechanical converters; when the control valve of the present invention is an electro-hydraulic servo valve, the first electro-mechanical converter 1 and the second electro-mechanical converter 14 are both servo electro-mechanical converters. The proportional electro-mechanical converter and the servo electro-mechanical converter provide power to drive the valve core 7 to move, and a controller can be further arranged to control the proportional electro-mechanical converter or the servo electro-mechanical converter to act as required.

Further, the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are in clearance fit with the grooves.

Further, the first lower oil outlet groove a1 and the first lower oil inlet groove p1 are both square grooves, the first lower oil outlet groove a1 and the first lower oil inlet groove p1 are arranged at intervals and aligned left and right, and the first lower low pressure groove t1 is a first circular ring groove surrounding the first lower oil inlet groove p1 and the first lower oil outlet groove a 1; the second lower oil outlet groove a5 and the second lower oil inlet groove p5 are both square grooves, the second lower oil outlet groove a5 and the second lower oil inlet groove p5 are arranged at intervals and aligned left and right, and the second lower low-pressure groove t6 is a second circular ring groove surrounding the second lower oil inlet groove p5 and the second lower oil outlet groove a 5; go up oil groove p3 with last oil groove a3 be square groove, just go up oil groove p3 with last oil groove a3 interval set up and control and align, last low pressure groove t3 be the encircleing go up oil groove p3 with last oil groove a3 around the circular annular groove of third.

Further, a plurality of lower low pressure holes t2 are spaced on the lower pressure compensation plate 3, and each of the lower low pressure holes t2 is arranged in a circle along the first lower low pressure groove t 1. Furthermore, a plurality of upper low pressure holes t4 are provided at intervals on the upper pressure compensation plate 4, and each upper low pressure hole t4 is arranged in a circle along the upper low pressure groove t 3. Furthermore, a plurality of middle and low pressure holes t5 are arranged on the valve core 7 at intervals, each middle and low pressure hole t5 is arranged in a circle along the valve core 7, and the middle and low pressure holes t5 are communicated with the upper low pressure groove t3 and the lower first lower low pressure groove t 1. Further, the oil inlet groove p2 is an elliptical groove or a rectangular groove.

Further, the valve port curve L includes a first line segment L1, a second line segment L2, and a third line segment L3 connected in sequence, the second line segment L2 is located on the right side of the first line segment L1 and the second line segment L3, a first break angle is formed between the first line segment L1 and the second line segment L2, a second break angle is formed between the third line segment L3 and the second line segment L2, and the first break angle and the second break angle are the same in size.

Furthermore, the middle oil outlet groove a2 comprises a rectangular groove on the left side and a trapezoidal groove on the right side, and the right side of the rectangular groove is communicated with the left side of the trapezoidal groove; the projection of the rectangular groove on the upper end face of the valve core 7 is rectangular, the projection of the trapezoidal groove on the upper end face of the valve core 7 is trapezoidal, and the right side edge of the rectangle is collinear with the lower bottom edge of the trapezoid.

Further, as shown in fig. 8, a projected area of the middle oil outlet groove a2 on the lower end surface of the valve element 7 is larger than a projected area of the first lower oil outlet groove a1 on the lower end surface of the valve element 7; the projection area of the middle oil inlet groove p2 on the lower end surface of the valve core 7 is smaller than the projection area of the first lower oil inlet groove p1 on the lower end surface of the valve core 7.

Or, well oil groove a2 can be discontinuous discrete form, promptly well oil groove a2 form by the combination of the bar groove e that a plurality of interval set up, bar groove e be parallel to each other, bar groove e from left right horizontal extension, the left end of bar groove e aligns, the length of bar groove e is inequality, as shown in fig. 8, is located the length of the bar groove e in the middle of the centre longest, and the length of the bar groove e of both sides diminishes gradually.

Specifically, the valve port curve L can be made into a continuous type or a discrete type, the continuous valve port curve L can realize the function of stepless regulation of flow gain, and the discrete valve port curve L can realize the function of stepped regulation of flow gain.

Further, the first sealing device and the second sealing device are sealing rings.

Specifically, the sealing rings on the first adjusting piston 5 and the second adjusting piston 6 are used for isolating oil on the upper end surface and the lower end surface of the first adjusting piston 5 or the second adjusting piston 6.

Furthermore, the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are both cylindrical, and the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are located by a pin shaft, a working plane and the like in the circumferential direction, so that the upper pressure compensation plate 4 and the lower pressure compensation plate 3 can only float in the vertical direction and cannot rotate. The valve core 7 can only slide left and right, back and forth and cannot rotate under the action of the first electro-mechanical converter 1 and the second electro-mechanical converter 14, so that the upper and lower edges of the right side of the middle oil outlet groove a2 of the valve core 7 forming the valve port can be respectively superposed with the left edge of the upper oil inlet groove p3 and the left edge of the lower oil inlet groove p1 in the original state, and the valve port is closed in the original state.

The working principle of the hydraulic valve in the embodiment is as follows:

the high-pressure oil in the high-pressure cavity P1 flows into the low-pressure cavity T1 through the gaps between the valve core 7 and the upper pressure compensation plate 4 and between the valve core 7 and the lower pressure compensation plate 3, and the same pressure oil films are respectively formed on the upper end surface and the lower end surface of the valve core 7; similarly, the oil in the working chamber a1 flows into the low pressure chamber T1 through the gaps between the valve core 7 and the upper pressure compensation plate 4 and between the valve core 7 and the lower pressure compensation plate 3, and the same pressure oil films are formed on the upper and lower end surfaces of the valve core 7.

The structural characteristics of the upper end surface and the lower end surface of the lower pressure compensation plate 3 are completely consistent, so that the pressures applied to the upper end surface and the lower end surface are equal, and the lower pressure compensation plate 3 is in a pressure balance state, so that the lower pressure compensation plate 3 is suspended.

The pressure oil film enables the gap pressure of the upper end surface and the lower end surface of the valve core 7 to be equal, and therefore the valve core 7 is suspended.

And a pressure oil film is formed between the lower end surface of the upper pressure compensation plate 4 and the upper end surface of the valve core 7. For the upper end surface of the upper pressure compensation plate 4, on one hand, the oil in the low pressure chamber T1 covers the upper end surface of the upper pressure compensation plate 4 through the upper low pressure hole T4 on the upper pressure compensation plate 4 and forms a low pressure oil film; on the other hand, the second pressure adjusting hole introduces high-pressure control oil to act on the second adjusting piston 6, the first pressure adjusting hole introduces working pressure control oil to act on the first adjusting piston 5, and both the first adjusting piston 5 and the second adjusting piston 6 act on the upper end surface of the upper pressure compensation plate 4 to form pressure compensation. The lower end surface of the upper pressure compensation plate 4 is subjected to a vertically upward acting force of a pressure oil film, the upper end surface of the upper pressure compensation plate 4 is subjected to a resultant force F of a vertically downward pressure of the first adjusting piston 5 and the second adjusting piston 6 and a pressure of the oil return port T acting on the lower end surface, the direction of the resultant force F is vertically downward, and an expression of the resultant force F of the upper end surface and the lower end surface of the upper pressure compensation plate 4 is ensured:

F＝M·S4+N·S3-P2·S2-A2·S1>0

in the formula, M is oil inlet pressure, N is oil outlet pressure, P2 is equivalent pressure of oil film distribution of valve core 7 end surface clearance pressure from a high-pressure cavity P1 to a low-pressure cavity T1, and A2 is equivalent pressure of oil film distribution of valve core 7 end surface clearance pressure from a working cavity A1 to a low-pressure cavity T1; s4 is the end surface area of the second adjusting piston 6, S3 is the end surface area of the first adjusting piston 5, S2 is the equivalent area of the valve element 7 end surface clearance pressure oil film from the high pressure chamber P1 to the low pressure chamber T1, and S1 is the equivalent area of the valve element 7 end surface clearance pressure oil film from the working chamber a1 to the low pressure chamber T1, as shown in fig. 5 and 6.

When F is greater than 0, the pressure of the upper end surface of the upper pressure compensation plate 4 is greater than that of the lower end surface, the upper pressure compensation plate 4 vertically moves downwards to press the valve core 7 and the lower pressure compensation plate 3, and the pressing force is F.

Assuming that the pressures of the oil inlet P and the oil outlet A are unchanged, the required resultant force F can be obtained by controlling the pressure variables P2 and A2 and the area variables S4, S3, S2 and S1, namely the pressing force of the upper pressure compensation plate 4 on the valve core 7, so that the gaps between the upper end surface of the valve core 7 and the lower end surface of the upper pressure compensation plate 4 and between the lower end surface of the valve core 7 and the upper end surface of the lower pressure compensation plate 3 can be adjusted, the gaps are reduced, the influence of leakage on the control flow can be reduced, and the flow control precision of the control valve is improved.

When the first electro-mechanical converter acts, the valve core 7 is pushed to move rightwards, meanwhile, when the second electro-mechanical converter 14 acts, the valve core 7 is pushed to move forwards and backwards, the valve core 7 performs combined reciprocating motion in two freedom directions in a valve core central plane, and the reciprocating motion rule of the valve core 7 is a composite set curve of the controller of the first electro-mechanical converter 1 and the controller of the first electro-mechanical converter 14; the valve port of the valve core is required to set a valve port curve L according to the working condition characteristics, the valve port of the valve core 7 is opened under the design motion rule of the first electro-mechanical converter 1 and the second electro-mechanical converter 14, the high pressure cavity P1 is communicated with the working cavity A1, namely, the oil inlet channel is communicated with the oil outlet channel, the valve core 7, the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are pressed under the action of resultant force F borne by the upper pressure compensation plate 4, and gaps between the upper end surface of the valve core 7 and the lower end surface of the upper pressure compensation plate 4 and between the lower end surface of the valve core 7 and the upper end surface of the lower pressure compensation plate 3 are reduced, so that the leakage is reduced, and the flow control precision. The valve core 7, the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are made of ceramic materials with high hardness, wear resistance, small friction coefficient and high surface smoothness, the friction coefficient of the end face is small, the friction force and the shearing force which need to be overcome when the valve core 7 is opened and slides are small, and the thrust of the first electro-mechanical converter 1 and the thrust of the second electro-mechanical converter 14 are small.

When the first electro-mechanical converter 1 and the second electro-mechanical converter 14 return to the original positions, the valve core 7 slides back to the original positions under the combined action of the first spring 10 and the second spring 17, and the valve port is closed according to the preset motion rule of the valve core 7. The high-pressure cavity P1 is not communicated with the working cavity A1, and the oil inlet channel is not communicated with the oil outlet channel, so that one working cycle is completed.

The equivalent concentrated force of the first electro-mechanical converter 1 acting on the left side plane of the valve core 7 is equal to the acting force of the first steel ball 8 of the left side first restraint device acting on the right side plane of the valve core, and the acting moments are equal in magnitude and opposite in direction; similarly, the equivalent concentrated force of the second electro-mechanical converter acting on the front side plane of the valve core is equal to the acting force of the second steel ball 15 of the rear side second restraint device acting on the rear side plane of the valve core, and the acting moments are equal in magnitude and opposite in direction; the first driving rod of the first restraint device and the second driving rod of the second restraint device respectively have guiding and restraining functions with the plane contacted with the valve core 7, and the valve core 7 is balanced in stress and moment in the moving process, cannot rotate and can only slide in the left-right and front-back two degrees of freedom of the central plane of the valve core 7.

The utility model discloses in set up pressure compensation device on unsteady case 7, adjust the size and the direction of making a concerted effort that pressure compensating plate 4 receives through pressure compensation device, make and go up pressure compensating plate 4 vertical downstream and compress tightly case 7 and holding down pressure compensating plate 3 to make the clearance between case 7 and last pressure compensating plate 4, case 7 and the holding down pressure compensating plate 3 reduce, reduce the influence of leaking to control flow, improve the flow control precision of this valve.

The utility model discloses a flat case 7's valve port curve L can design into function curve according to the operating mode requirement, the compound curve, the dysmorphism curve, various continuous curves such as experience curve, and simultaneously, first electricity-mechanical converter 1, second electricity-mechanical converter 2 can be about case 7 central plane, two degree of freedom directions are according to control strategy to the different motion law of different operating mode designs propelling movement case 7 of difference and are compound motion around, change case valve port open area gradient in succession, realize infinitely variable control electricity liquid proportion servo valve flow gain, the electricity liquid proportion servo valve control performance has been improved.

The valve port curve L of the plate-type valve element 7 of the present invention can also be made into a discrete type, as shown in fig. 8. The discrete valve port curve L is still consistent with the valve port curve L of the valve core shown in the figures 6 and 7, all discrete valve ports are communicated, pressure oil is prevented from crushing a partition plate between all valve ports, the distance between all discrete valve ports is reasonably distributed, and the function of adjusting flow gain in a stepped mode can be achieved.

1) in the embodiment of the application, the upper pressure compensation plate 4, the valve core 7 and the lower pressure compensation plate 3 which are stacked up and down are buckled to form an oil inlet channel, an oil outlet channel and an oil return channel, and when the valve core 7 deviates on a horizontal plane, the area gradient of a valve port communicating the oil inlet channel and the oil outlet channel can be changed; the valve core 7 is pushed to do compound motion in two freedom degree directions by arranging a first guiding constraint mechanism capable of driving the valve core 7 to move left and right and a second guiding constraint mechanism capable of driving the valve core to move front and back, and the opening area gradient of the valve port of the valve core 7 is continuously changed, so that the flow gain is changed, and the flow gain of the control valve is regulated and controlled. Because the first guide constraint mechanism and the second guide constraint mechanism of the embodiment of the application control and adjust the originally fixed flow gain of the control valve on the basis of normal flow or pressure control of a single control valve, the flow gain of the control valve is not limited by the mechanical structure of the control valve, meanwhile, the control mechanism has simple structure and small volume, overcomes the technical problems that the flow gain of the electro-hydraulic control valve is limited by the self-mechanical structure or the control system has large volume and complex control in the prior art, realizes the beneficial effect of greatly improving the dynamic performance of the electro-hydraulic control system, and because the continuity of the valve port continuous curve flow regulation is better, the flow has no obvious transient impact in the switching process, and the upper and lower clearances of the valve core are reduced under the pressure compensation effect through the pressure compensation plate, so that the control precision of the control valve can be effectively improved.

2) The upper pressure compensation plate 4 and the lower pressure compensation plate 3 are respectively arranged on the floating valve core 7, the pressure compensation device is arranged on the upper pressure compensation plate 4, the pressure compensation device is adjusted to enable the upper pressure compensation plate 4 to move downwards and press the valve core 7, so that the gap between the valve core 7 and the upper pressure compensation plate 4 and the gap between the valve core 7 and the lower pressure compensation plate 3 are reduced, the leakage amount through the gap is reduced, and the flow control precision of the control valve can be effectively improved.

3) The clearance between the upper end surface and the lower end surface of the valve core 7 and the clearance between the upper pressure compensation plate 4 and the lower pressure compensation plate 3 are reduced, and oil pollutants and particulate matters can be prevented from entering a working clearance, so that the valve core 7 is not easily scratched, abraded and stuck by the pollutants.

4) The valve port curve L can be made into a continuous type or a discrete type, the continuous valve port curve L can realize the function of stepless regulation of flow gain, and the discrete valve port curve L can realize the function of stepped regulation of flow gain.

Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention and not for limiting, and although the present invention has been described in detail with reference to the examples, those skilled in the art should understand that the technical solutions of the present invention can be modified or replaced by equivalents without departing from the spirit and scope of the technical solutions of the present invention, which should be covered by the scope of the claims of the present invention.

Claims

1. The utility model provides an electro-hydraulic control valve that can regulate and control flow gain which characterized in that: the electro-hydraulic control valve comprises an upper valve body (2) and a lower valve body (13) which are fixedly connected up and down, wherein a groove is formed in the lower surface of the upper valve body (2), and an upper pressure compensation plate (4) and a lower pressure compensation plate (3) which can only move up and down are sequentially arranged in the groove from top to bottom;

a valve core (7) is arranged between the upper pressure compensation plate (4) and the lower pressure compensation plate (3), and a first guide constraint mechanism for driving the valve core (7) to move along the left-right direction and a second guide constraint mechanism for driving the valve core (7) to move along the front-back direction are respectively arranged on the periphery of the valve core (7);

the first guiding constraint mechanism comprises a first electro-mechanical converter (1) and a first constraint device which are oppositely arranged along the left-right direction, and the first electro-mechanical converter (1) is positioned outside the upper valve body (2) and fixed on the left side surface of the upper valve body (2); the first electro-mechanical converter (1) is provided with a first driving rod which horizontally extends to the right and penetrates into the groove, and the first driving rod is abutted against the left side surface of the valve core (7) so as to drive the valve core (7) to move along the left-right direction; the first restraint device comprises a first baffle (12) and a first spring push rod (11), the first baffle (12) is fixed on the right side face of the upper valve body (2), the first spring push rod (11) horizontally penetrates through the first baffle (12) along the left-right direction, the right end of the first spring push rod (11) is in threaded connection with the first baffle (12), the left end of the first spring push rod (11) extends into the groove and is connected with a first spring pressure head (9) through a first spring (10), the first spring (10) can stretch out and draw back along the left-right direction, the first spring pressure head (9) is connected with a first pressure ball (8), and the first pressure ball (8) abuts against the right side face of the valve core (7);

the second guiding constraint mechanism comprises a second electromechanical converter (14) and a second constraint device which are oppositely arranged along the front-back direction, and the second electromechanical converter (14) is positioned outside the upper valve body (2) and fixed on the front side surface of the upper valve body (2); the second electro-mechanical converter (14) is provided with a second driving rod which horizontally penetrates into the groove, and the second driving rod is abutted against the front side surface of the valve core (7) so as to drive the valve core (7) to move along the front-back direction; the second restraint device comprises a second baffle plate (19) and a second spring push rod (18), the second baffle plate (19) is fixed on the rear side face of the upper valve body (2), the second spring push rod (18) horizontally penetrates through the second baffle plate (19) along the front-rear direction, the rear end of the second spring push rod (18) is in threaded connection with the second baffle plate (19), the front end of the second spring push rod (18) extends into the groove and is connected with a second spring pressure head (16) through a second spring (17), the second spring (17) can stretch out and draw back along the front-rear direction, the second spring pressure head (16) is connected with a second pressure ball (15), and the second pressure ball (15) abuts against the right side face of the valve core (7);

the lower surface of the upper pressure compensation plate (4) is respectively provided with an upper oil inlet groove (p3), an upper oil outlet groove (a3) and an upper low pressure groove (t 3);

the upper surface of the lower pressure compensation plate (3) is respectively provided with a first lower oil inlet groove (p1), a first lower oil outlet groove (a1) and a first lower low pressure groove (t 1); a second lower oil inlet groove (p5), a second lower oil outlet groove (a5) and a second lower low pressure groove (t6) are respectively arranged on the lower surface of the lower pressure compensation plate (3), wherein the second lower oil inlet groove (p5) and the first lower oil inlet groove (p1) are symmetrically arranged relative to the central cross section of the lower pressure compensation plate (3), the second lower oil outlet groove (a5) and the first lower oil outlet groove (a1) are symmetrically arranged relative to the central cross section of the lower pressure compensation plate (3), and the second lower low pressure groove (t6) and the first lower low pressure groove (t1) are symmetrically arranged relative to the central cross section of the lower pressure compensation plate (3); and the second lower oil inlet groove (p5) is communicated with the first lower oil inlet groove (p1) through a lower oil inlet hole (p4), the second lower oil outlet groove (a5) is communicated with the first lower oil outlet groove (a1) through a lower oil outlet hole (a4), and the second lower low pressure groove (t6) is communicated with the first lower low pressure groove (t1) through a lower low pressure hole (t 2); the valve core (7) is respectively provided with a middle oil inlet groove (p2), a middle oil outlet groove (a2) and a middle low-pressure hole (t5) which are vertically communicated, the right side of the middle oil outlet groove (a2), the left side of the upper oil inlet groove (p3) and the left side of the first lower oil inlet groove (p1) form a valve port, the projection of the right side edge of the middle oil outlet groove (a2) on the valve core (7) is a valve port curve (L), and the valve port curve (L) is a curve or a broken line;

the first lower oil inlet groove (p1) and the upper oil inlet groove (p3) are arranged in a vertically symmetrical manner, the first lower oil outlet groove (a1) and the upper oil outlet groove (a3) are arranged in a vertically symmetrical manner, and the first lower low-pressure groove (t1) and the upper low-pressure groove (t3) are arranged in a vertically symmetrical manner; the middle oil outlet groove (a2) and the middle oil inlet groove (p2) are arranged at left and right intervals, and the length of the middle oil outlet groove (a2) in the left and right direction is greater than the distance between the first lower oil outlet groove (a1) and the first lower oil inlet groove (p 1);

an oil inlet (P), an oil outlet (A) and an oil return port (T) are formed in the lower surface of the lower valve body (13), an oil inlet flow passage (P), an oil outlet flow passage (a) and a low-pressure flow passage (T) are formed in the lower valve body (13), the second lower oil inlet groove (P5) is communicated with the oil inlet (P) through the oil inlet flow passage (P), the second lower oil outlet groove (a5) is communicated with the oil outlet (A) through the oil outlet flow passage (a), and the second lower low-pressure groove (T6) is communicated with the oil return port (T) through the low-pressure flow passage (T);

the second lower oil inlet groove (P5), the lower oil inlet hole (P4), the first lower oil inlet groove (P1), the middle oil inlet groove (P2) and the upper oil inlet groove (P3) are aligned up and down and penetrate through to form a high-pressure cavity (P1); the second lower oil outlet groove (a5), the lower oil outlet hole (a4), the first lower oil outlet groove (a1), the middle oil outlet groove (a2) and the upper oil outlet groove (A3) are aligned up and down and penetrate through to form a working cavity (A1); the second lower low pressure groove (T6), the lower low pressure hole (T2), the first lower low pressure groove (T1), the middle and low pressure hole (T5) and the upper low pressure groove (T3) are aligned up and down and are communicated with each other to form a low pressure cavity (T1); the high-pressure cavity (P1) is communicated with the oil inlet (P) through the oil inlet flow passage (P) to form an oil inlet channel; the working cavity (A1) is communicated with the oil outlet (A) through the oil outlet flow passage (a) to form an oil outlet channel; the low-pressure cavity (T1) is communicated with the oil return port (T) through the low-pressure flow passage (T) to form an oil return passage;

a plurality of upper low-pressure holes (t4) are arranged in the upper pressure compensation plate (4), the bottom end openings of the upper low-pressure holes (t4) extend into the upper low-pressure groove (t3) and are communicated with the upper low-pressure groove (t3), and the top end openings of the upper low-pressure holes (t4) are positioned on the upper surface of the upper pressure compensation plate (4);

the control valve also comprises a pressure compensation device, the pressure compensation device comprises a first mounting groove and a second mounting groove which are arranged on the lower surface of the upper valve body (2), the first mounting groove and the upper surface of the upper pressure compensation plate (4) enclose a first adjusting cavity, and the second mounting groove and the upper surface of the upper pressure compensation plate (4) enclose a second adjusting cavity; a first adjusting piston (5) only capable of moving up and down is arranged in the first adjusting cavity, a second adjusting piston (6) only capable of moving up and down is arranged in the second adjusting cavity, a first sealing device is arranged between the inner wall surface of the first adjusting cavity and the outer peripheral surface of the first adjusting piston (5), and a second sealing device is arranged between the inner wall surface of the second adjusting cavity and the outer peripheral surface of the second adjusting piston (6);

the upper valve body (2) is also provided with a first pressure adjusting hole for inputting high-pressure control oil above the first adjusting piston (5) and a second pressure adjusting hole for inputting working pressure control oil above the second adjusting piston (6); the bottom end of the first pressure adjusting hole is communicated with the bottom of the first mounting groove, the top end of the first pressure adjusting hole is located on the upper surface of the valve body (2) and is communicated with an oil outlet (A), the bottom end of the second pressure adjusting hole is communicated with the bottom of the second mounting groove, and the top end of the second pressure adjusting hole is located on the upper surface of the valve body (2) and is communicated with an oil inlet (P).

2. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: the first lower oil outlet groove (a1) and the first lower oil inlet groove (p1) are both square grooves, the first lower oil outlet groove (a1) and the first lower oil inlet groove (p1) are arranged at intervals and are aligned left and right, and the first lower low-pressure groove (t1) is a first circular ring groove which surrounds the first lower oil inlet groove (p1) and the first lower oil outlet groove (a 1);

the second lower oil outlet groove (a5) and the second lower oil inlet groove (p5) are both square grooves, the second lower oil outlet groove (a5) and the second lower oil inlet groove (p5) are arranged at intervals and are aligned left and right, and the second lower low-pressure groove (t6) is a second circular ring groove surrounding the second lower oil inlet groove (p5) and the second lower oil outlet groove (a 5);

go up oil groove (p3) with last oil groove (a3) be square groove, just go up oil groove (p3) with last oil groove (a3) interval set up and control and align, last low-pressure groove (t3) encircle go up oil groove (p3) with last oil groove (a3) around the circular annular groove of third.

3. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: the middle oil inlet groove (p2) is an elliptical groove or a rectangular groove.

4. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: the valve port curve (L) comprises a first line segment (L1), a second line segment (L2) and a third line segment (L3) which are connected in sequence, wherein the second line segment (L2) is positioned on the right side of the first line segment (L1) and the second line segment (L2); the first line segment (L1) and the second line segment (L2) have a first break angle therebetween, the third line segment (L3) and the second line segment (L2) have a second break angle therebetween, and the first break angle and the second break angle are the same in size.

5. The adjustable flow gain electro-hydraulic control valve of claim 4, wherein: the middle oil outlet groove (a2) comprises a rectangular groove positioned on the left side and a trapezoidal groove positioned on the right side, and the right side of the rectangular groove is communicated with the left side of the trapezoidal groove; the projection of the rectangular groove on the upper end face of the valve core (7) is rectangular, the projection of the trapezoidal groove on the upper end face of the valve core (7) is trapezoidal, and the right side edge of the rectangle is collinear with the lower bottom edge of the trapezoid.

6. The adjustable flow gain electro-hydraulic control valve of claim 4, wherein: well oil groove (a2) form by the combination of bar groove (e) that a plurality of interval set up, bar groove (e) be parallel to each other, bar groove (e) from left right side horizontal extension, the left end in bar groove (e) is mutually aligned, the length in bar groove (e) is inequality.

7. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: a plurality of upper low-pressure holes (t4) are arranged on the upper pressure compensation plate (4) at intervals, and each upper low-pressure hole (t4) is arranged in a circle around the upper low-pressure groove (t 3).

8. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: the projection area of the middle oil outlet groove (a2) on the lower end surface of the valve core (7) is larger than the projection area of the first lower oil outlet groove (a1) on the lower end surface of the valve core (7); the projection area of the middle oil inlet groove (p2) on the lower end surface of the valve core (7) is smaller than that of the first lower oil inlet groove (p1) on the lower end surface of the valve core (7).

9. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: the valve core (7) is provided with a plurality of middle and low pressure holes (t5) at intervals, the middle and low pressure holes (t5) are arranged in a circle along the valve core (7), and the middle and low pressure holes (t5) are communicated with the upper low pressure groove (t3) above and the first lower low pressure groove (t1) below.

10. The adjustable flow gain electro-hydraulic control valve of claim 1, wherein: the valve core (7) is plate-shaped, and the front side, the rear side, the left side and the right side of the valve core (7) are respectively provided with a vertical plane at equal angular intervals; the first driving rod and the second driving rod respectively abut against the vertical planes on the left side and the front side; the first pressure ball (8) is in point contact with the vertical plane on the right side of the valve core (7), and the second pressure ball (15) is in point contact with the vertical plane on the rear side of the valve core (7).