Bidirectional inverse proportional flow valve

Abstract

The invention belongs to the technical field of valves, and discloses a bidirectional inverse proportional flow valve. The bidirectional inverse proportional flow valve comprises a valve sleeve, a proportional valve element, an electromagnetic driving assembly and a compensation valve element. A valve port A and a valve port B are formed in the valve sleeve. One end of the proportional valve element is arranged in the valve sleeve and provided with a valve element hole, and fluid can flow to the valve port B through the valve port A and the valve element hole in sequence or flow to the valve port A through the valve port B and the valve element hole in sequence. The electromagnetic driving assembly is assembled on the valve sleeve and used for pushing the proportional valve element to axially move in the valve sleeve. The compensation valve element is arranged in the valve sleeve and can move in two directions in the axial direction of the valve sleeve under the action of the pressure difference between the valve port A and the valve port B. According to the bidirectional inverse proportion flow valve, bidirectional inverse proportion adjustment and pressure compensation can be achieved, so that the bidirectional inverse proportion flow valve can be applied to occasions needing bidirectional proportion adjustment and pressure compensation, the application scene range is wide, and universality is high.

Description

Technical Field

[0001] The invention relates to the technical field of valves, and in particular to a bidirectional inverse proportional flow valve. Background Art

[0002] Proportional flow valves can achieve proportional control of the pressure, flow and other parameters of the hydraulic system under the action of proportional solenoids. The so-called proportional control is to control the movement distance of the proportional valve core by changing the current value passed through the internal coil of the proportional solenoid through the controller, thereby changing the opening amount of the proportional valve port to achieve proportional control. Existing proportional flow valves can only achieve inverse proportional control and pressure compensation when the fluid flows in one direction. They cannot be used in situations where bidirectional proportional adjustment and pressure compensation are required, and the application scenarios are relatively limited.

[0003] Therefore, there is an urgent need to provide a bidirectional inverse proportional flow valve to solve the above problems. Summary of the invention

[0004] The object of the present invention is to provide a bidirectional inverse proportional flow valve, which can realize bidirectional proportional control and pressure compensation and has a wider application scenario.

[0005] To achieve this object, the present invention adopts the following technical solutions:

[0006] Bidirectional inverse proportional flow valve, comprising:

[0007] A valve sleeve, wherein a valve port A and a valve port B are formed on the valve sleeve;

[0008] A proportional valve core, one end of which is disposed in the valve sleeve and is provided with a valve core hole, so that the fluid can flow to the valve port B through the valve port A and the valve core hole in sequence, or flow to the valve port A through the valve port B and the valve core hole in sequence;

[0009] An electromagnetic drive assembly, mounted on the valve sleeve and used to push the proportional valve core to move axially in the valve sleeve;

[0010] The compensating valve core is arranged in the valve sleeve and can move bidirectionally along the axial direction of the valve sleeve under the pressure difference between the valve port A and the valve port B.

[0011] As an optional scheme, it also includes a limit seat and a valve seat, the valve seat is arranged at one end of the valve sleeve, at least part of the compensation valve core is penetrated in the valve seat, the valve seat is provided with a valve seat hole connected with the valve port B, one end of the proportional valve core is penetrated in the valve seat, the limit seat is penetrated in the other end of the valve sleeve, the limit seat is provided with a connecting hole and a connecting cavity connected with the valve port A, when the electromagnetic drive component is powered off, the valve port A can be connected with the valve port B through the connecting hole, the connecting cavity, the valve core hole and the valve seat hole.

[0012] As an optional solution, the valve core hole and the valve seat hole are in a normally connected state.

[0013] As an optional solution, when the electromagnetic drive assembly is powered on and when the control current gradually increases, the conduction area between the valve core hole and the valve seat hole gradually decreases.

[0014] As an optional scheme, a first limit boss is protruding on the limit seat, and a second limit boss is protruding on the valve seat. One end of the compensation valve core is sleeved on the outside of the limit seat and can abut against the first limit boss, and the other end of the compensation valve core is sleeved on the outside of the valve seat and can abut against the second limit boss.

[0015] As an optional scheme, it also includes a compensation spring, which is arranged in the compensation valve core and sleeved on the outside of the limit seat, and two limit blocks arranged at intervals are provided in the compensation valve core, one of the limit blocks can abut against the limit seat, and the other limit block can abut against the valve seat, and the compensation spring is located between the two limit blocks, one end of the compensation spring abuts against the limit block close to the limit seat, and the other end of the compensation spring abuts against the limit block close to the valve seat.

[0016] As an optional solution, a limiting step is protruded inside the compensation valve core, and a side of the limiting block away from the compensation spring abuts against the limiting step;

[0017] And / or, the inner side wall of the compensation valve core is recessed with a limiting groove surrounding the circumference thereof, a wire retaining ring is placed in the limiting groove, and the side of the limiting block away from the compensation spring abuts against the wire retaining ring.

[0018] As an optional solution, the valve port A and the valve port B are opened on the peripheral side of the valve sleeve.

[0019] As an optional solution, a valve port C is further provided at one axial end of the valve sleeve, and the valve port C can be blocked.

[0020] As an optional solution, it also includes a spring seat and a proportional spring. The spring seat is limited by a retaining ring to one end of the proportional valve core close to the electromagnetic drive assembly. The proportional spring is sleeved outside the proportional valve core and pressed tightly between the spring seat and the valve seat.

[0021] Beneficial effects of the present invention:

[0022] The bidirectional inverse proportional flow valve provided by the present invention has a compensating valve core that can move in both directions. Regardless of whether the hydraulic oil flows from valve port A to valve port B or from valve port B to valve port A, inverse proportional regulation and pressure compensation can be achieved. Therefore, bidirectional inverse proportional regulation and pressure compensation can be achieved, so that it can be used in situations where bidirectional proportional regulation and pressure compensation are required. The application scenarios are relatively wide and the versatility is relatively strong. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 is a cross-sectional view of a bidirectional inverse proportional flow valve provided by an embodiment of the present invention;

[0024] Figure 2 is a first cross-sectional view of a bidirectional inverse proportional flow valve provided by an embodiment of the present invention with the electromagnetic drive component hidden;

[0025] Figure 3 This is a second cross-sectional view of the bidirectional inverse proportional flow valve provided by an embodiment of the present invention with the electromagnetic drive component hidden.

[0026] In the figure:

[0027] 1. Limit seat; 1a. Connecting hole; 1b. Connecting cavity; 1c. First limit boss; 2. Wire retaining ring; 4. Compensating valve core; 4a. Right annular surface; 4b. Left annular surface; 4c. Limit step; 4d. Limit groove; 5. Limit block; 6. Valve sleeve; 7. Compensating spring; 10. Valve seat; 10a. Valve seat hole; 10b. Second limit boss; 13. Proportional valve core; 13a. Valve core hole; 15. Proportional spring; 18. Spring seat; 19. Push rod; 20. Magnetic sleeve; 21. Moving iron; 22. Tail end; 23. Coil. DETAILED DESCRIPTION

[0028] The present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It is to be understood that the specific embodiments described herein are only used to explain the present invention, rather than to limit the present invention. It should also be noted that, for ease of description, only parts related to the present invention, rather than all structures, are shown in the accompanying drawings.

[0029] In the description of the present invention, unless otherwise clearly specified and limited, the terms "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0030] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0031] In the description of this embodiment, the terms "upper", "lower", "right", etc., directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description and simplification of operation, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are only used to distinguish in the description and have no special meaning.

[0032] like Figures 1 to 3 As shown, this embodiment provides a two-way inverse proportional flow valve, including a valve sleeve 6, a proportional valve core 13, an electromagnetic drive assembly and a compensation valve core 4. The valve sleeve 6 is provided with a valve port A and a valve port B. One end of the proportional valve core 13 is arranged in the valve sleeve 6 and is provided with a valve core hole 13a. The fluid can flow to the valve port B through the valve port A and the valve core hole 13a in sequence. At this time, the valve port A is the oil inlet, the valve port B is the oil outlet, and a load is externally connected; or, the fluid can also flow to the valve port A through the valve port B and the valve core hole 13a in sequence. At this time, the valve port B is the oil inlet, the valve port A is the oil outlet, and a load is externally connected; the electromagnetic drive assembly is assembled on the valve sleeve 6, and is used to push the proportional valve core 13 to move axially in the valve sleeve 6. The compensation valve core 4 is arranged in the valve sleeve 6, and can move bidirectionally along the axial direction of the valve sleeve 6 under the pressure difference between the valve port A and the valve port B to adjust the opening amount of the valve port A and the valve port B. A compensation spring 7 is arranged inside the compensation valve core 4. When the compensation valve core 4 moves left and right, the compensation spring 7 can be compressed.

[0033] refer to Figure 2, when valve port A is the oil inlet, and when the electromagnetic drive assembly is powered off, the hydraulic oil enters the valve sleeve 6 through valve port A, and then passes through the valve core hole 13a on the proportional valve core 13 and then flows out through valve port B. At the same time, the hydraulic pressure at valve port A will act on the right annular surface 4a of the compensation valve core 4 (assuming the hydraulic pressure is F1), and the hydraulic pressure at valve port B will act on the left annular surface 4b of the compensation valve core 4 (assuming the hydraulic pressure is F2). At this time, due to the pressure difference, that is, F1>F2, the compensation valve core 4 will move to the left to adjust the opening amount of valve ports A and valve ports B. During the movement, the compensation valve core 4 compresses the compensation spring 7 to the left (assuming the spring force is △P). At this time, the following approximate equation can be formed: △P=F1-F2, and the compensation valve core 4 reaches a new balance. In this process, the position of the proportional valve core 13 remains unchanged, and the compensation valve core 4 keeps the pressure difference balanced at all times, so the flow of valve port A remains basically stable and is not affected by the fluctuation of its downstream load. When the electromagnetic drive assembly is powered on, the output end of the electromagnetic drive assembly pushes the proportional valve core 13 to move rightward, so that the conduction area between the valve core hole 13a of the proportional valve core 13 and the valve port B is gradually reduced until it is closed, and the output flow rate will also gradually decrease to zero output.

[0034] Similarly, reference Figure 3 , when valve port B is the oil inlet, and when the electromagnetic drive assembly is powered off, the hydraulic oil enters the valve sleeve 6 through valve port B and the valve core hole 13a on the proportional valve core 13, and then flows out through valve port A. At the same time, the hydraulic pressure at valve port B will act on the left annular surface 4b of the compensation valve core 4 (assuming the hydraulic pressure is F1), and the hydraulic pressure at valve port A will act on the right annular surface 4a of the compensation valve core 4 (assuming the hydraulic pressure is F2). At this time, due to the pressure difference, that is, F1>F2, the compensation valve core 4 will move to the right to adjust the opening amount of valve ports A and B. During the movement, the compensation valve core 4 compresses the compensation spring 7 to the right (assuming the spring force is △P). At this time, the following approximate equation can be formed: △P=F1-F2, and the compensation valve core 4 reaches a new balance. In this process, the position of the proportional valve core 13 remains unchanged, and the compensation valve core 4 keeps the pressure difference balanced at all times, so the flow of valve port B remains basically stable and is not affected by the fluctuation of its downstream load. When the electromagnetic drive assembly is powered on, the output end of the electromagnetic drive assembly pushes the proportional valve core 13 to move rightward, so that the conduction area between the valve core hole 13a of the proportional valve core 13 and the valve port B is gradually reduced until it is closed, and the output flow rate will also gradually decrease to zero output.

[0035] It can be seen that the bidirectional inverse proportional flow valve provided in this embodiment has a compensating valve core 4 that can move in both directions. Regardless of whether the hydraulic oil flows from valve port A to valve port B or from valve port B to valve port A, inverse proportional regulation and pressure compensation can be achieved. Therefore, bidirectional inverse proportional regulation and pressure compensation can be achieved, so that it can be used in situations where bidirectional proportional regulation and pressure compensation are required. It has a wide range of application scenarios and strong versatility.

[0036] Among them, Figure 1 As shown, the electromagnetic drive assembly specifically includes a coil 23, a magnetic sleeve 20, a tail bell 22, a moving iron 21 and a push rod 19. One end of the magnetic sleeve 20 is fixedly sleeved on the outside of the valve sleeve 6, the coil 23 is installed on the outside of the magnetic sleeve 20, a concave cavity is provided in the magnetic sleeve 20, and the moving iron 21 is slidably installed in the concave cavity. The tail bell 22 is installed at the left end of the magnetic sleeve 20 and is used to limit the leftward movement of the moving iron 21. One end of the push rod 19 is connected to the moving iron 21, and the other end passes through the magnetic sleeve 20 and abuts against the end of the proportional valve core 13.

[0037] Furthermore, the two-way inverse proportional flow valve also includes a valve seat 10, a spring seat 18 and a proportional spring 15. The valve seat 10 is arranged in the valve sleeve 6. A valve seat hole 10a connected to the valve port B is opened on the valve seat 10. The valve core hole 13a can be connected to the valve port B through the valve seat hole 10a. One end of the proportional valve core 13 is penetrated into the valve seat 10, and the other end is against the push rod 19. The spring seat 18 is limited to one end of the proportional valve core 13 close to the electromagnetic drive component by a retaining ring. The proportional spring 15 is sleeved on the outside of the proportional valve core 13 and pressed tightly between the spring seat 18 and the valve seat 10.

[0038] like Figure 1 As shown in the figure, when the coil 23 is not energized, the proportional spring 15 pushes the proportional valve core 13 to the left to the left limit position, and the movable iron 21 is also in the left limit position. At this time, the valve core hole 13a on the proportional valve core 13 and the valve seat hole 10a on the valve seat 10 are fully connected. When the coil 23 is energized, under the action of the electromagnetic force, the movable iron 21 is driven to move to the right, and the movable iron 21 pushes the push rod 19, and then pushes the proportional valve core 13 to move to the right to overcome the elastic force of the proportional spring 15. As the proportional valve core 13 moves to the right, the conductive area of ​​the valve core hole 13a on the proportional valve core 13 and the valve seat hole 10a on the valve seat 10 is gradually reduced until they are completely staggered, as shown in the figure. Figure 2 shown.

[0039] Furthermore, if Figure 1 and Figure 2As shown, the bidirectional inverse proportional flow valve further includes a limit seat 1, at least part of the valve seat 10 is arranged at one end in the valve sleeve 6, the limit seat 1 is arranged at the other end in the valve sleeve 6, one end of the proportional valve core 13 is penetrated in the valve seat 10, a valve seat hole 10a communicating with the valve port B is provided on the valve seat 10, a connecting hole 1a and a connecting cavity 1b communicating with the valve port A are provided on the limit seat 1, and when the electromagnetic drive assembly is powered off, the valve port A can be connected to the valve port B via the connecting hole 1a, the connecting cavity 1b, the valve core hole 13a and the valve seat hole 10a in sequence. When the coil 23 is powered off, the fluid can flow to the valve port B via the valve port A, the connecting hole 1a, the connecting cavity 1b, the valve core hole 13a and the valve seat hole 10a in sequence, or can flow to the valve port A via the valve port B, the valve seat hole 10a, the valve core hole 13a, the connecting cavity 1b and the connecting hole 1a in sequence.

[0040] In this embodiment, the valve core hole 13a and the valve seat hole 10a are in a normally open state. That is, when the coil 23 is powered off, the valve core hole 13a and the valve seat hole 10a are always in a fully open state, so that the valve does not need to be powered on during normal use, which effectively saves energy and avoids the problem of valve performance failure caused by heating of the coil 23 due to long-term power supply during use. When the valve needs to be closed, current can be turned on.

[0041] Further, in this embodiment, when the coil 23 of the electromagnetic drive assembly is energized, and when the control current gradually increases, the conduction area between the valve core hole 13a and the valve seat hole 10a gradually decreases. Among them, the "conductivity area" here refers to the interception area through which the fluid can pass when the valve core hole 13a and the valve seat hole 10a are relative or partially relative. In other words, the magnitude of the magnetic force exerted on the moving iron 21 is related to the magnitude of the input current in the coil 23. The greater the input current, the greater the magnetic force, and the farther the push rod 19 moves to the right. As the current gradually increases, the push rod 19 gradually moves to the right, causing the conduction area between the valve core hole 13a and the valve seat hole 10a to gradually decrease, and the flow from valve port A to valve port B or valve port B to valve port A naturally gradually decreases. Therefore, the output flow is inversely proportional to the control current, that is, the greater the control current, the smaller the output flow.

[0042] like Figure 2 As shown, in this embodiment, valve port A and valve port B are provided on the circumferential side of the valve sleeve 6. Furthermore, a valve port C is provided at one axial end of the valve sleeve 6. When the two-way inverse proportional flow valve is in use, the valve port C is blocked. In an optional embodiment, as Figure 2 As shown, the limit seat 1 is provided with a first limit convex shoulder 1c, the valve seat 10 is provided with a second limit convex shoulder 10b, one end of the compensation valve core 4 is sleeved outside the limit seat 1 and can abut against the first limit convex shoulder 1c, and the other end of the compensation valve core 4 is sleeved outside the valve seat 10 and can abut against the second limit convex shoulder 10b. Figure 3, the first limit convex shoulder 1c can limit the right limit position of the compensation valve core 4. When the compensation valve core 4 reaches the right limit position, the right annular surface 4a of the compensation valve core 4 abuts against the first limit convex shoulder 1c. At this time, in the non-powered state, the compensation valve core 4 completely blocks the valve port A, and the valve port C can be fully connected with the valve port B through the connecting cavity 1b, the valve core hole 13a and the valve seat hole 10a, and is cut off from the valve port A. Figure 2 The second limiting boss 10b can limit the left limit position of the compensating valve core 4. When the compensating valve core 4 reaches the left limit position, the left annular surface 4b of the compensating valve core 4 abuts against the second limiting boss 10b. At this time, when the maximum current is passed, the compensating valve core 4 completely blocks the valve port B, the valve port C is fully connected to the valve port A, and is cut off from the valve port B.

[0043] Furthermore, the two-way inverse proportional flow valve further includes a compensation spring 7, which is arranged in the compensation valve core 4 and sleeved outside the limit seat 1. The compensation valve core 4 is provided with two spaced limit blocks 5 along its axial direction. Both limit blocks 5 are sleeved outside the limit seat 1, one of which can abut against the limit seat 1, and the other limit block 5 can abut against the valve seat 10. The compensation spring 7 is located between the two limit blocks 5, one end of the compensation spring 7 abuts against the limit block 5 close to the limit seat 1, and the other end of the compensation spring 7 abuts against the limit block 5 close to the valve seat 10. Figure 2 As shown in FIG. 1 , when the compensation valve core 4 moves to the left, it can drive the limit block 5 on the right to move to the left, while the limit block 5 on the left abuts against the valve seat 10 and thus remains stationary, thereby compressing the compensation spring 7, and finally balancing the force on the compensation valve core 4 to achieve pressure compensation; Figure 3 As shown, when the compensation valve core 4 moves to the right, it can drive the limit block 5 on the left to move to the right, while the limit block 5 on the right abuts against the step surface of the limit seat 1 and thus remains stationary, thereby compressing the compensation spring 7, and finally balancing the force on the compensation valve core 4 to achieve pressure compensation.

[0044] Specifically, Figure 2 As shown, a limiting step 4c is convexly provided on the right side of the inner side of the compensation valve core 4, and the limiting block 5 on the right side, which is away from the compensation spring 7, abuts against the limiting step 4c. In this way, when the compensation valve core 4 moves to the left, the limiting step 4c provided on the inner side thereof can drive the limiting block 5 on the right side to move to the left, thereby realizing the compression of the compensation spring 7.

[0045] Furthermore, if Figure 1 and Figure 3As shown, the inner wall of the left side of the compensation valve core 4 is concavely provided with a limiting groove 4d surrounding the circumference thereof, and a wire retaining ring 2 is placed in the limiting groove 4d, and the limiting block 5 on the left side away from the side of the compensation spring 7 abuts against the wire retaining ring 2. In this way, when the compensation valve core 4 moves to the right, the wire retaining ring 2 arranged on the inner side thereof can drive the limiting block 5 on the left side to move to the right, thereby realizing the compression of the compensation spring 7.

[0046] In another optional embodiment, a limit step 4c may be provided on both the left and right sides of the compensation valve core 4 to drive the limit block 5 on the corresponding side to move. In another optional embodiment, a wire retaining ring 2 may be provided on both the left and right sides of the compensation valve core 4 to drive the limit block 5 on the corresponding side to move. In another optional embodiment, a limit step 4c may be provided on the left side of the compensation valve core 4, and a wire retaining ring 2 may be provided on the right side to drive the limit block 5 on the corresponding side to move, which is not specifically limited here.

[0047] The working principle of the bidirectional inverse proportional flow valve provided in this embodiment is:

[0048] refer to Figure 2 , when the valve port A is the oil inlet, and when the coil 23 is powered off, the proportional spring 15 pushes the proportional valve core 13 to the left to the left limit position, and the movable iron 21 is also in the left limit position. At this time, the valve core hole 13a on the throttle valve core and the valve seat hole 10a on the valve seat 10 are fully connected, and the hydraulic oil can flow through the valve port A, the connecting hole 1a, the connecting cavity 1b, the valve core hole 13a and the valve seat hole 10a in sequence, and finally the oil is discharged through the valve port B. At the same time, the hydraulic pressure at the valve port A will act on the right annular surface 4a of the compensation valve core 4 (assuming that the hydraulic pressure is F1), and the hydraulic pressure at the valve port B will act on the left annular surface 4b of the compensation valve core 4 (assuming that the hydraulic pressure is F2). At this time, due to the pressure difference, that is, F1>F2, the compensation valve core 4 will move to the left to adjust the opening amount of valve port A and valve port B. During the movement, the compensation valve core 4 drives the right limit block 5 to move to the left through the limit step 4c set therein, while the left limit block 5 abuts against the valve seat 10, so it remains motionless, and the compensation spring 7 will be compressed (assuming the spring force is △P). At this time, the following approximate equation can be formed: △P=F1-F2, and the compensation valve core 4 reaches a new balance. In this process, the position of the proportional valve core 13 remains unchanged, and the compensation valve core 4 keeps the pressure difference in dynamic balance at all times, so the flow of valve port A remains basically stable and is not affected by the fluctuation of its downstream load.

[0049] When the coil 23 is energized, the electromagnetic force drives the moving iron 21 to move rightward, and the moving iron 21 pushes the push rod 19, which in turn pushes the proportional valve core 13 to move rightward to overcome the elastic force of the proportional spring 15. As the proportional valve core 13 moves rightward, the conducting area between the valve core hole 13a on the proportional valve core 13 and the valve seat hole 10a on the valve seat 10 gradually decreases until they are completely offset, and the output flow rate will also gradually decrease to zero output.

[0050] Similarly, reference Figure 3 , when the valve port B is the oil inlet, and when the coil 23 is powered off, the proportional spring 15 pushes the proportional valve core 13 to the left to the left limit position, and the moving iron 21 is also in the left limit position. At this time, the valve core hole 13a on the throttle valve core and the valve seat hole 10a on the valve seat 10 are fully connected, and the hydraulic oil can flow through the valve port B, the valve seat hole 10a, the valve core hole 13a, the connecting cavity 1b and the connecting hole 1a in sequence, and finally the oil is discharged through the valve port A. At the same time, the hydraulic pressure at the valve port B will act on the left annular surface 4b of the compensation valve core 4 (assuming the hydraulic pressure is F1), and the hydraulic pressure at the valve port A will act on the right annular surface 4a of the compensation valve core 4 (assuming the hydraulic pressure is F2). At this time, due to the pressure difference, that is, F1>F2, the compensation valve core 4 will move to the right to adjust the opening amount of valve port A and valve port B. During the movement, the compensation valve core 4 drives the limit block 5 on the left to move to the right through the wire retaining ring 2 set therein, while the limit block 5 on the right abuts against the step surface of the limit seat 1, so it remains motionless, and the compensation spring 7 will be compressed (assuming the spring force is △P). At this time, the following approximate equation can be formed: △P=F1-F2, and the compensation valve core 4 reaches a new balance. In this process, the position of the proportional valve core 13 remains unchanged, and the compensation valve core 4 keeps the pressure difference balanced at all times, so the flow of valve port B remains basically stable and is not affected by the fluctuation of its downstream load.

[0051] When the coil 23 is energized, the electromagnetic force drives the moving iron 21 to move rightward, and the moving iron 21 pushes the push rod 19, thereby pushing the proportional valve core 13 to move rightward to overcome the elastic force of the proportional spring 15. As the proportional valve core 13 moves rightward, the conducting area between the valve core hole 13a on the proportional valve core 13 and the valve seat hole 10a on the valve seat 10 gradually decreases until they are completely offset, and the output flow rate will also gradually decrease to zero output.

[0052] To sum up, the bidirectional inverse proportional flow valve provided in this embodiment has a compensating valve core 4 that can move in both directions. Regardless of whether the hydraulic oil flows from valve port A to valve port B or from valve port B to valve port A, inverse proportional regulation and pressure compensation can be achieved. Therefore, bidirectional inverse proportional regulation and pressure compensation can be achieved, so that it can be used in situations where bidirectional proportional regulation and pressure compensation are required. It has a wide range of application scenarios and strong versatility.

[0053] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. For those skilled in the art, various obvious changes, readjustments and substitutions can be made without departing from the protection scope of the present invention. It is not necessary and impossible to list all the embodiments here. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the claims of the present invention.

Claims

1. Bidirectional inverse proportional flow valve, characterized in that: include: A valve sleeve (6), wherein the valve sleeve (6) is provided with a valve port A and a valve port B; A proportional valve core (13), one end of which is disposed in the valve sleeve (6) and is provided with a valve core hole (13a), so that the fluid can flow to the valve port B through the valve port A and the valve core hole (13a) in sequence, or flow to the valve port A through the valve port B and the valve core hole (13a) in sequence; An electromagnetic drive assembly, mounted on the valve sleeve (6) and used to push the proportional valve core (13) to move axially in the valve sleeve (6); The compensating valve core (4) is arranged in the valve sleeve (6) and can move bidirectionally along the axial direction of the valve sleeve (6) under the action of the pressure difference between the valve port A and the valve port B.

2. The bidirectional inverse proportional flow valve according to claim 1, characterized in that: It also includes a limit seat (1) and a valve seat (10), wherein at least a portion of the valve seat (10) is disposed at one end of the valve sleeve (6), and a valve seat hole (10a) communicating with the valve port B is provided on the valve seat (10), one end of the proportional valve core (13) is passed through the valve seat (10), and the limit seat (1) is disposed at the other end of the valve sleeve (6), and a connecting hole (1a) and a connecting cavity (1b) communicating with the valve port A are provided on the limit seat (1), and when the electromagnetic drive assembly is powered off, the valve port A can be communicated with the valve port B via the connecting hole (1a), the connecting cavity (1b), the valve core hole (13a) and the valve seat hole (10a).

3. The bidirectional inverse proportional flow valve according to claim 2, characterized in that: The valve core hole (13a) and the valve seat hole (10a) are in a normally open state.

4. The bidirectional inverse proportional flow valve according to claim 2, characterized in that: When the electromagnetic drive assembly is powered on and when the control current gradually increases, the conduction area between the valve core hole (13a) and the valve seat hole (10a) gradually decreases.

5. The bidirectional inverse proportional flow valve according to claim 2, characterized in that: The limit seat (1) is provided with a first limit convex shoulder (1c), the valve seat (10) is provided with a second limit convex shoulder (10b), one end of the compensation valve core (4) is sleeved outside the limit seat (1) and can abut against the first limit convex shoulder (1c), and the other end of the compensation valve core (4) is sleeved outside the valve seat (10) and can abut against the second limit convex shoulder (10b).

6. The bidirectional inverse proportional flow valve according to claim 5, characterized in that: The invention also comprises a compensation spring (7), wherein the compensation spring (7) is arranged in the compensation valve core (4) and sleeved on the outside of the limit seat (1); two limit blocks (5) arranged at intervals are arranged in the compensation valve core (4); one of the limit blocks (5) can abut against the limit seat (1), and the other limit block (5) can abut against the valve seat (10); the compensation spring (7) is located between the two limit blocks (5); one end of the compensation spring (7) abuts against the limit block (5) close to the limit seat (1), and the other end of the compensation spring (7) abuts against the limit block (5) close to the valve seat (10).

7. The bidirectional inverse proportional flow valve according to claim 6, characterized in that: A limiting step (4c) is protrudingly provided inside the compensation valve core (4), and a side of the limiting block (5) away from the compensation spring (7) abuts against the limiting step (4c); And / or, the inner side wall of the compensation valve core (4) is recessed with a limiting groove (4d) surrounding the circumference thereof, a steel wire retaining ring (2) is accommodated in the limiting groove (4d), and the side of the limiting block (5) away from the compensation spring (7) abuts against the steel wire retaining ring (2).

8. The bidirectional inverse proportional flow valve according to any one of claims 1 to 7, characterized in that: The valve port A and the valve port B are opened on the peripheral side of the valve sleeve (6).

9. The bidirectional inverse proportional flow valve according to claim 8, characterized in that: A valve port C is also formed at one axial end of the valve sleeve (6), and the valve port C can be blocked.

10. The bidirectional inverse proportional flow valve according to any one of claims 2 to 7, characterized in that: The invention also comprises a spring seat (18) and a proportional spring (15); the spring seat (18) is located at one end of the proportional valve core (13) close to the electromagnetic drive assembly through a retaining ring; the proportional spring (15) is sleeved outside the proportional valve core (13) and pressed tightly between the spring seat (18) and the valve seat (10).

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