Bidirectional inverse proportional flow valve

Abstract

The utility model belongs to the technical field of valves, and discloses a bidirectional inverse proportion 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. The bidirectional inverse proportion flow valve provided by the utility model can realize bidirectional inverse proportion adjustment and pressure compensation, so that the bidirectional inverse proportion flow valve can be applied to occasions requiring bidirectional proportion adjustment and pressure compensation, and is wide in application scene and high in universality.

Description

Technical Field

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

[0002] Proportional flow valves, driven by a proportional solenoid, can achieve proportional control of hydraulic system parameters such as pressure and flow. Proportional control involves controlling the movement of the proportional valve spool by varying the current flowing through the solenoid's internal coil via a controller, thereby changing the opening of the valve orifice. Existing proportional flow valves can only achieve inverse proportional control and pressure compensation for fluid flow in one direction. They are not suitable for applications requiring bidirectional proportional adjustment and pressure compensation, limiting their application scenarios.

[0003] Therefore, there is an urgent need to provide a bidirectional inverse proportional flow valve to solve the above problems. Utility Model Content

[0004] The purpose of the utility model 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 purpose, the present invention adopts the following technical solutions:

[0006] Bidirectional inverse proportional flow valve, including:

[0007] A valve sleeve, wherein the valve sleeve is provided with a valve port A and a valve port B;

[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, assembled on the valve sleeve and used to push the proportional valve core to move axially within the valve sleeve;

[0010] The compensating valve core is arranged in the valve sleeve and can move in two directions 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 alternative solution, it further includes a limit seat and a valve seat. The valve seat is arranged at one end inside the valve sleeve. At least part of the compensation spool penetrates through the valve seat. A valve seat hole communicating with the valve port B is formed in the valve seat. One end of the proportional spool penetrates through the valve seat. The limit seat penetrates through the other end inside the valve sleeve. A communication hole and a communication cavity communicating with the valve port A are formed in the limit seat. When the electromagnetic drive assembly is powered off, the valve port A can communicate with the valve port B through the communication hole, the communication cavity, the spool hole and the valve seat hole.

[0012] As an alternative solution, the spool hole and the valve seat hole are in a normally open state.

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

[0014] As an alternative solution, a first limit shoulder protrudes from the limit seat, and a second limit shoulder protrudes from the valve seat. One end of the compensation spool is sleeved outside the limit seat and can abut against the first limit shoulder, and the other end of the compensation spool is sleeved outside the valve seat and can abut against the second limit shoulder.

[0015] As an alternative solution, it further includes a compensation spring. The compensation spring is arranged inside the compensation spool and sleeved outside the limit seat. Two spaced limit blocks are arranged inside the compensation spool. One of the limit blocks can abut against the limit seat, and the other limit block can abut against the valve seat. 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 alternative solution, a limit step protrudes inside the compensation spool, and the side of the limit block away from the compensation spring abuts against the limit step.

[0017] And / or, a circumferentially surrounding limit groove is recessed in the inner side wall of the compensation spool, and a wire retaining ring is accommodated in the limit groove. The side of the limit block away from the compensation spring abuts against the wire retaining ring.

[0018] As an alternative solution, the valve port A and the valve port B are formed on the circumferential side of the valve sleeve.

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

[0020] As an alternative solution, it further includes a spring seat and a proportional spring. The spring seat is limited to one end of the proportional spool close to the electromagnetic drive assembly by a retaining ring. The proportional spring is sleeved outside the proportional spool and abuts between the spring seat and the valve seat.

[0021] Advantages of the present utility model:

[0022] For the two-way inverse proportional flow valve provided by the present utility model, the compensation spool can move bidirectionally. Whether the hydraulic oil flows from port A to port B or from port B to port A, the inverse proportional adjustment and pressure compensation functions can be realized. Therefore, two-way inverse proportional adjustment and pressure compensation can be achieved, so that it can be applied to occasions that require two-way proportional adjustment and pressure compensation at the same time. The application scenario is relatively wide and the universality is strong. Description of the drawings

[0023] Figure 1 is a cross-sectional view of the two-way inverse proportional flow valve provided by an embodiment of the present utility model;

[0024] Figure 2 is the first cross-sectional view of the two-way inverse proportional flow valve provided by an embodiment of the present utility model with the electromagnetic drive assembly hidden;

[0025] Figure 3 is the second cross-sectional view of the two-way inverse proportional flow valve provided by an embodiment of the present utility model with the electromagnetic drive assembly hidden.

[0026] In the figure:

[0027] 1. Limit seat; 1a. Communication hole; 1b. Communication cavity; 1c. First limit shoulder; 2. Wire retaining ring; 4. Compensation spool; 4a. Right-side annular surface; 4b. Left-side annular surface; 4c. Limit step; 4d. Limit groove; 5. Limit block; 6. Valve sleeve; 7. Compensation spring; 10. Valve seat; 10a. Valve seat hole; 10b. Second limit shoulder; 13. Proportional spool; 13a. Spool hole; 15. Proportional spring; 18. Spring seat; 19. Push rod; 20. Magnetic conduction sleeve; 21. Moving iron; 22. Tail collar; 23. Coil. Detailed implementation manners

[0028] The present utility model will be further described in detail below with reference to the drawings and embodiments. It can be understood that the specific embodiments described herein are only used to explain the present utility model, rather than limiting the present utility model. Additionally, it should be noted that for the sake of description, only parts related to the present utility model are shown in the drawings, rather than all the structures.

[0029] In the description of the present utility model, unless otherwise clearly defined and limited, the terms "connected", "connected to", and "fixed" shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two components or the interaction relationship between two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0030] In the present utility model, unless otherwise clearly defined and limited, the first feature being "above" or "below" the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through other features between them. Moreover, the first feature being "above", "over", and "on top of" the second feature includes that the first feature is directly above and obliquely above the second feature, or merely indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature being "below", "beneath", and "underneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or merely indicates that the horizontal height of the first feature is lower than that of the second feature.

[0031] In the description of this embodiment, the orientation or positional relationships such as "above", "below", "right", etc. are based on the orientation or positional relationship shown in the drawings. It is only for the convenience of description and simplifying the operation, rather than indicating or implying that the device or component referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.

[0032] As Figures 1 to 3 shown, this embodiment provides a bidirectional inverse proportional flow valve, which includes a valve sleeve 6, a proportional spool 13, an electromagnetic drive assembly, and a compensation spool 4. The valve sleeve 6 is provided with a valve port A and a valve port B. One end of the proportional spool 13 is arranged inside the valve sleeve 6 and is provided with a spool hole 13a. The fluid can flow to the valve port B through the valve port A and the spool 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 spool 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 spool 13 to axially move inside the valve sleeve 6. The compensation spool 4 is arranged inside the valve sleeve 6 and can axially move bidirectionally along the valve sleeve 6 under the pressure difference between the valve port A and the valve port B to adjust the opening amounts of the valve port A and the valve port B. A compensation spring 7 is arranged inside the compensation spool 4. When the compensation spool 4 moves left and right, the compensation spring 7 can be compressed.

[0033] Refer to Figure 2, when the valve port A is the oil inlet and the electromagnetic drive assembly is powered off, the hydraulic oil enters the inside of the valve sleeve 6 through the valve port A, then passes through the valve core hole 13a on the proportional valve core 13 and exits through the valve port B. At the same time, the hydraulic pressure at the valve port A acts on the right annular surface 4a of the compensation valve core 4 (assuming the hydraulic pressure is F1), and the hydraulic pressure at the valve port B acts 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 amounts of the valve port A and the valve port B. During the movement, the compensation valve core 4 compresses the compensation spring 7 to the left (assuming the spring force is ΔP). At this time, an approximate equation can be formed: ΔP = F1 - F2, and the compensation valve core 4 reaches a new balance. During this process, the position of the proportional valve core 13 remains unchanged, and the compensation valve core 4 keeps the pressure difference balanced all the time. Therefore, the flow rate of the valve port A remains basically stable and is not affected by the downstream load fluctuation. When the electromagnetic drive assembly is powered on, the output end of the electromagnetic drive assembly pushes the proportional valve core 13 to move to the right, so that the conduction area between the valve core hole 13a of the proportional valve core 13 and the valve port B gradually decreases until it is closed, and the output flow rate will also gradually decrease to zero output.

[0034] Similarly, referring to Figure 3 , when the valve port B is the oil inlet and the electromagnetic drive assembly is powered off, the hydraulic oil enters the inside of the valve sleeve 6 through the valve port B and the valve core hole 13a on the proportional valve core 13, and then exits through the valve port A. At the same time, the hydraulic pressure at the valve port B acts 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 acts 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 amounts of the valve port A and the valve port B. During the movement, the compensation valve core 4 compresses the compensation spring 7 to the right (assuming the spring force is ΔP). At this time, an approximate equation can be formed: ΔP = F1 - F2, and the compensation valve core 4 reaches a new balance. During this process, the position of the proportional valve core 13 remains unchanged, and the compensation valve core 4 keeps the pressure difference balanced all the time. Therefore, the flow rate of the valve port B remains basically stable and is not affected by the downstream load fluctuation. When the electromagnetic drive assembly is powered on, the output end of the electromagnetic drive assembly pushes the proportional valve core 13 to move to the right, so that the conduction area between the valve core hole 13a of the proportional valve core 13 and the valve port B gradually decreases until it is closed, and the output flow rate will also gradually decrease to zero output.

[0035] It can be seen from this 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, such as 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, and 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 passed through 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 assembly by a retaining ring. The proportional spring 15 is sleeved on the outside of the proportional valve core 13 and tightly pressed between the spring seat 18 and the valve seat 10.

[0038] like Figure 1 As shown, 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 electromagnetic force, the movable iron 21 is driven to move to the right. The movable iron 21 pushes the push rod 19, and then pushes the proportional valve core 13 to move to the right, overcoming 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 gradually decreases until they are completely offset, as shown in FIG. Figure 2 shown.

[0039] Furthermore, if Figure 1 and Figure 2As shown, the two-way inverse proportional flow valve further includes a limit seat 1. At least part of the valve seat 10 is disposed at one end within the valve sleeve 6, and the limit seat 1 is disposed at the other end within the valve sleeve 6. One end of the proportional spool 13 passes through the valve seat 10. A valve seat hole 10a communicating with the valve port B is formed on the valve seat 10. A communication hole 1a and a communication cavity 1b communicating with the valve port A are formed on the limit seat 1. When the electromagnetic drive assembly is powered off, the valve port A can communicate with the valve port B in sequence through the communication hole 1a, the communication cavity 1b, the spool hole 13a, and the valve seat hole 10a. When the coil 23 is powered off, the fluid can flow to the valve port B in sequence through the valve port A, the communication hole 1a, the communication cavity 1b, the spool hole 13a, and the valve seat hole 10a, or can flow to the valve port A in sequence through the valve port B, the valve seat hole 10a, the spool hole 13a, the communication cavity 1b, and the communication hole 1a.

[0040] In this embodiment, the spool hole 13a and the valve seat hole 10a are in a normally open state. That is to say, when the coil 23 is powered off, the spool 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, achieving effective energy saving and avoiding the problem that the coil 23 heats up due to long-term power-on during use, resulting in the failure of the valve performance. When it is necessary to close the valve, current can be applied.

[0041] Furthermore, in this embodiment, when the coil 23 of the electromagnetic drive assembly is powered on and when the control current gradually increases, the conduction area between the spool hole 13a and the valve seat hole 10a gradually decreases. Here, the "conduction area" refers to the cross-sectional area through which the fluid can pass when the spool hole 13a and the valve seat hole 10a are opposite or partially opposite. That is to say, the magnitude of the magnetic force received by the moving iron 21 is related to the magnitude of the input current in the coil 23. The larger 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 spool hole 13a and the valve seat hole 10a to gradually decrease. Naturally, the flow rate from the valve port A to the valve port B or from the valve port B to the valve port A also gradually decreases. Therefore, the output flow rate is inversely proportional to the control current, that is, the larger the control current, the smaller the output flow rate.

[0042] As Figure 2 shown, in this embodiment, the valve ports A and B are formed on the circumferential side of the valve sleeve 6. Furthermore, a valve port C is also formed 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 shown, a first limit shoulder 1c protrudes from the limit seat 1, and a second limit shoulder 10b protrudes from the valve seat 10. One end of the compensation spool 4 is sleeved outside the limit seat 1 and can abut against the first limit shoulder 1c, and the other end of the compensation spool 4 is sleeved outside the valve seat 10 and can abut against the second limit shoulder 10b. Refer to Figure 3, the first limiting shoulder 1c can limit the right extreme position of the compensation spool 4. When the compensation spool 4 reaches the right extreme position, the right annular surface 4a of the compensation spool 4 abuts against the first limiting shoulder 1c. At this time, in the non-powered state, the compensation spool 4 completely blocks the valve port A, and the valve port C can be fully communicated with the valve port B through the communication cavity 1b, the spool hole 13a, and the valve seat hole 10a, and is cut off from the valve port A. Refer to Figure 2 , the second limiting shoulder 10b can limit the left extreme position of the compensation spool 4. When the compensation spool 4 reaches the left extreme position, the left annular surface 4b of the compensation spool 4 abuts against the second limiting shoulder 10b. At this time, in the state of applying the maximum current, the compensation spool 4 completely blocks the valve port B, and the valve port C is fully communicated with 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. The compensation spring 7 is arranged inside the compensation spool 4 and sleeved outside the limiting seat 1. Two spaced limiting blocks 5 are axially arranged inside the compensation spool 4. Both of the two limiting blocks 5 are sleeved outside the limiting seat 1. One of the limiting blocks 5 can abut against the limiting seat 1, and the other limiting block 5 can abut against the valve seat 10. The compensation spring 7 is located between the two limiting blocks 5. One end of the compensation spring 7 abuts against the limiting block 5 close to the limiting seat 1, and the other end of the compensation spring 7 abuts against the limiting block 5 close to the valve seat 10. As Figure 2 shown, when the compensation spool 4 moves leftward, it can drive the right limiting block 5 to move leftward, while the left limiting block 5 abuts against the valve seat 10 and thus remains stationary, thereby compressing the compensation spring 7, and finally making the compensation spool 4 in force balance to achieve pressure compensation; as Figure 3 shown, when the compensation spool 4 moves rightward, it can drive the left limiting block 5 to move rightward, while the right limiting block 5 abuts against the step surface of the limiting seat 1 and thus remains stationary, thereby compressing the compensation spring 7, and finally making the compensation spool 4 in force balance to achieve pressure compensation.

[0044] Specifically, as Figure 2 shown, a limiting step 4c is convexly provided on the inner right side of the compensation spool 4. The side of the right limiting block 5 away from the compensation spring 7 abuts against the limiting step 4c. With such a setting, when the compensation spool 4 moves leftward, it can drive the right limiting block 5 to move leftward through the limiting step 4c provided on its inner side, thereby realizing the compression of the compensation spring 7.

[0045] Furthermore, as Figure 1 and Figure 3As shown, a limiting groove 4d that circumferentially surrounds is recessed in the inner side wall on the left side of the compensation spool 4. A circlip 2 is disposed in the limiting groove 4d. The side of the limiting block 5 on the left side away from the compensation spring 7 abuts against the circlip 2. With such a setting, when the compensation spool 4 moves rightward, the limiting block 5 on the left side can be driven to move rightward through the circlip 2 disposed inside it, so as to compress the compensation spring 7.

[0046] In another alternative embodiment, limiting steps 4c can be provided on both the left and right sides inside the compensation spool 4 to drive the limiting blocks 5 on the corresponding sides to move. In another alternative embodiment, circlips 2 can also be provided on both the left and right sides inside the compensation spool 4 to drive the limiting blocks 5 on the corresponding sides to move. In another alternative embodiment, a limiting step 4c can be provided on the left side inside the compensation spool 4 and a circlip 2 can be provided on the right side to drive the limiting blocks 5 on the corresponding sides to move, and specific limitations are not made here.

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

[0048] Refer to Figure 2 , when the valve port A is the oil inlet and when the coil 23 is de-energized, the proportional spring 15 pushes the proportional spool 13 to the left extreme position, and the moving iron 21 is also in the left limiting position. At this time, the spool hole 13a on the throttle spool is fully communicated with the valve seat hole 10a on the valve seat 10. The hydraulic oil can flow through the valve port A, the communication hole 1a, the communication cavity 1b, the spool hole 13a, and the valve seat hole 10a in sequence, and finally exits through the valve port B. At the same time, the hydraulic pressure at the valve port A acts on the right annular surface 4a of the compensation spool 4 (assuming the hydraulic pressure is F1), and the hydraulic pressure at the valve port B acts on the left annular surface 4b of the compensation spool 4 (assuming the hydraulic pressure is F2). At this time, due to the pressure difference effect, that is, F1 > F2, the compensation spool 4 will move to the left to adjust the opening amounts of the valve port A and the valve port B. During the movement, the compensation spool 4 drives the limiting block 5 on the right side to move leftward through the limiting step 4c provided inside it, while the limiting block 5 on the left side abuts against the valve seat 10, so it remains stationary, and the compensation spring 7 will be compressed (assuming the spring force is △P). At this time, such an approximate equation can be formed: △P = F1 - F2, and the compensation spool 4 reaches a new balance. During this process, the position of the proportional spool 13 remains unchanged, and the compensation spool 4 keeps the pressure difference in dynamic balance all the time. Therefore, the flow rate of the valve port A remains basically stable and is not affected by the downstream load fluctuation.

[0049] When the coil 23 is energized, the electromagnetic force drives the movable iron 21 to move rightward, and the movable iron 21 pushes the push rod 19, which in turn pushes the proportional valve core 13 to move rightward against 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 valve port B is the oil inlet and coil 23 is de-energized, proportional spring 15 pushes proportional valve core 13 leftward to the left limit position, placing movable iron 21 in the left limit position. At this point, valve core hole 13a in the throttle valve core and valve seat hole 10a in valve seat 10 are fully connected. Hydraulic oil can flow sequentially through valve port B, valve seat hole 10a, valve core hole 13a, communication chamber 1b, and communication hole 1a, ultimately exiting through valve port A. Simultaneously, the hydraulic pressure at valve port B acts on the left annular surface 4b of compensation valve core 4 (assuming hydraulic pressure F1), while the hydraulic pressure at valve port A acts on the right annular surface 4a of compensation valve core 4 (assuming hydraulic pressure F2). At this point, due to the pressure differential (i.e., F1 > F2), the compensating valve core 4 moves rightward to adjust the openings of valve ports A and B. During this movement, the compensating valve core 4, via the wire retaining ring 2 located within it, drives the left-hand stopper 5 to the right, while the right-hand stopper 5 abuts the stepped surface of the stopper seat 1, thus remaining stationary. Compensating spring 7 is compressed (assuming the spring force is ΔP). At this point, the following approximate equation can be formed: ΔP = F1 - F2, and the compensating valve core 4 reaches a new equilibrium. During this process, the proportional valve core 13 remains in position, and the compensating valve core 4 maintains a constant pressure balance. Therefore, the flow rate at valve port B remains essentially stable, unaffected by downstream load fluctuations.

[0051] When the coil 23 is energized, the electromagnetic force drives the movable iron 21 to move to the right. The movable iron 21 pushes the push rod 19, and then pushes the proportional valve core 13 to move to the right, overcoming the elastic force of the proportional spring 15. As the proportional valve core 13 moves to the right, the conductive 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, it can achieve inverse proportional regulation and pressure compensation. Therefore, bidirectional inverse proportional regulation and pressure compensation can be achieved, so 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-mentioned embodiments of the present utility model are merely examples for clearly illustrating the present utility model, rather than limitations on the implementation manners of the present utility model. For those of ordinary skill in the art, various obvious changes, re-adjustments and substitutions can be made without departing from the protection scope of the present utility model. It is not necessary and impossible to enumerate all the implementation manners here. Any modifications, equivalent substitutions and improvements made within the spirit and principle of the present utility model shall be included within the protection scope of the claims of the present utility model.

Claims

1. Two-way inverse proportional flow valve, characterized in that, Comprising: A valve sleeve (6), on which a valve port A and a valve port B are provided; A proportional spool (13), one end of which is arranged inside the valve sleeve (6) and is provided with a spool hole (13a), and fluid can flow from the valve port A and the spool hole (13a) to the valve port B in sequence, or flow from the valve port B and the spool hole (13a) to the valve port A in sequence; An electromagnetic drive assembly, assembled on the valve sleeve (6) and used to push the proportional spool (13) to axially move inside the valve sleeve (6); A compensation spool (4), arranged inside the valve sleeve (6) and capable of axially moving bidirectionally along the valve sleeve (6) under 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 further includes a limit seat (1) and a valve seat (10), at least part of the valve seat (10) is arranged at one end inside the valve sleeve (6), a valve seat hole (10a) communicating with the valve port B is provided on the valve seat (10), one end of the proportional spool (13) penetrates into the valve seat (10), the limit seat (1) is arranged at the other end inside the valve sleeve (6), a communication hole (1a) and a communication cavity (1b) communicating with the valve port A are provided on the limit seat (1), when the electromagnetic drive assembly is powered off, the valve port A can be communicated with the valve port B through the communication hole (1a), the communication cavity (1b), the spool hole (13a) and the valve seat hole (10a).

3. The bi-directional inverse proportional flow valve according to claim 2, wherein The spool hole (13a) and the valve seat hole (10a) are in a normally open state.

4. The bi-directional inverse proportional flow valve according to claim 2, wherein When the electromagnetic drive assembly is powered on and when the control current gradually increases, the conduction area between the spool hole (13a) and the valve seat hole (10a) gradually decreases.

5. The two-way inverse proportional flow valve according to claim 2, wherein The limit seat (1) protrudes with a first limit shoulder (1c), the valve seat (10) protrudes with a second limit shoulder (10b), one end of the compensation spool (4) is sleeved outside the limit seat (1) and can abut against the first limit shoulder (1c), and the other end of the compensation spool (4) is sleeved outside the valve seat (10) and can abut against the second limit shoulder (10b).

6. The bidirectional inverse proportional flow valve according to claim 5, characterized in that, It further includes a compensation spring (7), the compensation spring (7) is arranged inside the compensation spool (4) and sleeved outside the limit seat (1), two spaced limit blocks (5) are arranged inside the compensation spool (4), one of the limit blocks (5) can abut against the limit seat (1), 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 bi-directional inverse proportional flow valve according to claim 6, wherein A limit step (4c) protrudes inside the compensation spool (4), and the side of the limit block (5) away from the compensation spring (7) abuts against the limit step (4c); And / or, a limiting groove (4d) surrounding the inner side wall of the compensation valve core (4) along its circumferential direction is recessed, a wire snap ring (2) is disposed in the limiting groove (4d), and one side of the limiting block (5) away from the compensation spring (7) abuts against the wire snap ring (2).

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

9. The two-way inverse proportional flow valve according to claim 8, characterized in that, A valve port C is further opened at one axial end of the valve sleeve (6), and the valve port C can be blocked.

10. The bi-directional inverse proportional flow valve according to any one of claims 2-7, characterized in that, It further includes a spring seat (18) and a proportional spring (15). The spring seat (18) is limited at one end of the proportional valve core (13) close to the electromagnetic drive assembly through a snap ring. The proportional spring (15) is sleeved outside the proportional valve core (13) and abuts tightly between the spring seat (18) and the valve seat (10).

Images