A proportional valve with dynamic compensation function

Abstract

The present invention relates to the technical field of proportional valves, and specifically to a proportional valve with a dynamic compensation function, comprising a valve seat, a proportional electromagnet arranged on the valve seat, a valve core assembly and a pressure regulating mechanism. An active valve core and a passive valve core are arranged in the valve seat, wherein a first flow port is provided on the active valve core and a second flow port is provided on the passive valve core, and an adjustable throttle port is formed in the overlapping area of the two. The angle of the active valve core is directly controlled by the proportional electromagnet, while the passive valve core is linked to the valve seat outlet pressure through a pressure trigger component and driven by a pressure execution component. When the outlet pressure fluctuates, the passive valve core can automatically adjust the rotation angle relative to the active valve core, thereby dynamically adjusting the opening of the throttle port, thereby solving the problem that the proportional electromagnet in the existing proportional valve is easily interfered with by environmental factors such as current, voltage fluctuations and temperature, resulting in inaccurate control of the valve core opening by the proportional electromagnet, thereby affecting the outlet pressure of the proportional valve.

Description

Technical Field

[0001] The present invention relates to the technical field of proportional valves, and in particular to a proportional valve with a dynamic compensation function. Background Art

[0002] As an important fluid control component, proportional valves are widely used in industrial automation, hydraulic systems, engineering machinery, and other fields. Their core function is to precisely adjust the valve opening through electrical signals, thereby achieving continuous control of flow or pressure. In the proportional valve's drive mechanism, the proportional solenoid is a key actuator. It generates electromagnetic force by receiving current signals from the controller, pushing the valve core to achieve the desired opening ratio. However, in practical applications, the performance of the proportional solenoid is easily affected by various external factors, resulting in a decrease in the accuracy of valve opening control and affecting the stability and reliability of the system.

[0003] First, the linear relationship between the proportional solenoid's driving force and input current is fundamental to ensuring accurate valve opening control. However, when the control current is too low, the solenoid's magnetic induction strength is insufficient, potentially resulting in insufficient driving force on the valve spool, preventing the preset valve opening and causing flow or pressure regulation deviations. Conversely, if the current is too high, the solenoid's driving force may be excessive due to magnetic saturation, causing the valve spool to overshoot or oscillate, thereby affecting control accuracy and response speed. Furthermore, fluctuations in the power supply voltage can indirectly affect the stability of the current signal, further exacerbating the unpredictability of valve opening control.

[0004] Secondly, changes in ambient temperature can significantly affect the performance of proportional solenoids. Rising temperatures can increase the resistance of the solenoid coil, reducing the effective current and weakening the electromagnetic force output. High temperatures can also alter the magnetic permeability of the magnetic material, further affecting the solenoid's response characteristics. Conversely, in low-temperature environments, the solenoid's mechanical components (such as the spring and valve core) may experience increased frictional resistance due to material contraction or reduced lubrication performance. This can cause sluggish valve core movement and affect the dynamic adjustment accuracy of the valve opening.

[0005] In summary, under complex working conditions, the proportional solenoid of the existing proportional valve is easily disturbed by environmental factors such as current, voltage fluctuations and temperature, resulting in inaccurate proportional control of the valve core opening by the proportional solenoid, which in turn affects the outlet pressure of the proportional valve. Summary of the Invention

[0006] In response to the problems existing in the prior art, a proportional valve with a dynamic compensation function is provided, wherein an active valve core and a passive valve core are arranged in the valve seat, wherein a first flow port is opened on the active valve core, and a second flow port is opened on the passive valve core, and an adjustable throttle port is formed in the overlapping area of the two. The angle of the active valve core is directly controlled by a proportional electromagnet, while the passive valve core is linked to the valve seat outlet pressure through a pressure trigger component and driven by a pressure actuator component. When the outlet pressure fluctuates, the passive valve core can automatically adjust the rotation angle relative to the active valve core, thereby dynamically adjusting the opening of the throttle port, solving the problem that the proportional electromagnet in the existing proportional valve is easily affected by environmental factors such as current, voltage fluctuations and temperature, resulting in inaccurate proportional control of the valve core opening by the proportional electromagnet, thereby affecting the outlet pressure of the proportional valve.

[0007] To address the problems of the prior art, the present invention provides a proportional valve with dynamic compensation, comprising a valve seat, a proportional solenoid disposed on the valve seat, a valve core assembly, and a pressure regulating mechanism. The valve core assembly includes a coaxially arranged active valve core and a passive valve core. The active valve core is transmission-connected to the armature of the proportional solenoid, and the passive valve core is rotatable relative to the active valve core. The active valve core is provided with a first flow port, and the passive valve core is provided with a second flow port. The overlapping area of the first flow port and the second flow port constitutes a controlled throttle. The pressure regulating mechanism includes a pressure actuator disposed in the valve seat near an inlet of the valve seat and transmission-connected to the passive valve core; a pressure trigger assembly disposed in the valve seat near an outlet of the valve seat; and a transmission rod, with its ends respectively connected to the pressure actuator and the pressure trigger assembly. When the outlet pressure of the valve seat is lower than a set value, the pressure trigger assembly drives the pressure actuator via the transmission rod to cause the passive valve core to rotate in a direction increasing the throttle opening. When the outlet pressure of the valve seat is higher than the set value, the pressure trigger assembly drives the pressure actuator via the transmission rod to cause the passive valve core to rotate in a direction decreasing the throttle opening.

[0008] Preferably, a separator seat is provided in the valve seat, which separates the inner cavity of the valve seat into an upstream cavity close to the inlet and a downstream cavity close to the outlet; the active valve core is rotatably supported on the end surface of the separator seat close to the downstream cavity; the passive valve core is rotatably supported on the end surface of the separator seat close to the upstream cavity; and the transmission rod slides axially through the separator seat.

[0009] Preferably, the pressure trigger assembly includes: a pressure-sensitive cylinder, which is arranged in the downstream chamber; a piston, which is slidably arranged in the pressure-sensitive cylinder, dividing the inner chamber of the pressure-sensitive cylinder into a pressure chamber and a back-pressure chamber, and the pressure chamber is connected to the valve seat outlet; a reset spring, which is arranged in the back-pressure chamber and is used to provide a reset force for the piston; the piston is fixedly connected to the transmission rod, and when the outlet pressure changes, the piston displaces axially and drives the transmission rod to slide, thereby driving the passive valve core to rotate through the pressure execution assembly.

[0010] Preferably, the pressure actuator assembly includes an actuator ring slidably arranged in the upstream chamber, the actuator ring is connected to the transmission rod, the inner circumference of the actuator ring is provided with a guide pin extending radially thereof, the surface of the passive valve core is provided with a curved guide groove, the guide pin extends into the curved guide groove and slides with it, when the transmission rod moves axially, the actuator ring is driven to move axially along the transmission shaft, and the linear motion is converted into the rotational motion of the passive valve core through the cooperation of the guide pin and the curved guide groove.

[0011] Preferably, the pressure trigger assembly also includes a maintaining spring arranged in the pressure chamber. The maintaining spring cooperates with the return spring to keep the piston in the middle position of the inner cavity of the pressure sensing cylinder under the state of no pressure difference. When the pressure at the valve seat outlet decreases, the piston moves toward the pressure chamber under the combined action of the elastic force of the return spring and the reduction in pressure in the pressure chamber; when the pressure at the valve seat outlet increases, the piston moves toward the back pressure chamber under the combined action of the elastic force of the maintaining spring and the increase in pressure in the pressure chamber.

[0012] Preferably, the pressure trigger assembly also includes an adjusting cylinder threadedly connected to the inner wall of the valve seat, and the adjusting cylinder includes: an operating end located outside the valve seat, for receiving a rotational driving force; a connecting end extending into the interior of the valve seat, forming an axially limited but relatively rotatable fitting relationship with the end of the pressure-sensing cylinder; when the adjusting cylinder is rotated, the connecting end pushes the pressure-sensing cylinder to move axially along the valve seat to change the initial position of the piston.

[0013] Preferably, a fixed ring is provided at one end of the pressure-sensing cylinder facing the valve seat outlet, and a rotating ring rotatably connected to the pressure-sensing ring is formed at one end of the regulating cylinder facing the pressure-sensing cylinder.

[0014] Preferably, a fixing cylinder is further provided in the valve seat, a chamber for installing the pressure-sensing cylinder is formed between the outer wall of the fixing cylinder and the inner wall of the valve seat, and a connecting ring with a hole is provided between the inner end of the fixing cylinder and the inner wall of the valve seat.

[0015] Preferably, a sealing ring is provided at the position where the transmission rod passes through the partition seat.

[0016] Preferably, a connecting shaft is provided at one end of the active valve core facing the valve seat outlet, a gear is provided on the connecting shaft, the armature of the proportional solenoid extends into the valve seat and is provided with a rack, and the rack is meshed with the gear.

[0017] Compared with the prior art, the present invention has the following advantages:

[0018] The present application arranges an active valve core and a passive valve core in the valve seat, wherein a first flow port is provided on the active valve core and a second flow port is provided on the passive valve core, and the overlapping area of the two forms an adjustable throttle port. The angle of the active valve core is directly controlled by the proportional electromagnet, while the passive valve core is linked to the valve seat outlet pressure through a pressure trigger assembly and driven by a pressure actuator assembly. When the outlet pressure fluctuates, the passive valve core can automatically adjust the rotation angle relative to the active valve core, thereby dynamically adjusting the opening of the throttle port. This structure ensures that the final opening of the valve throttle port not only depends on the control signal of the proportional electromagnet, but can also be compensated according to the actual pressure changes, effectively reducing the influence of environmental factors such as current, voltage fluctuations and temperature on the proportional electromagnet control, thereby solving the problem that the outlet pressure of the proportional valve fluctuates due to the opening fluctuation. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a stereoscopic diagram of a proportional valve with dynamic compensation function according to the present invention.

[0020] Figure 2 It is a three-dimensional cross-sectional view of a proportional valve with a dynamic compensation function according to the present invention.

[0021] Figure 3 It is a cross-sectional view of a proportional valve with dynamic compensation function according to the present invention.

[0022] Figure 4 yes Figure 3 A partial enlarged view of point A.

[0023] Figure 5 yes Figure 3 A partial enlarged view of point B.

[0024] Figure 6 yes Figure 3 A partial enlarged view of point C.

[0025] Figure 7 It is a schematic diagram of the internal structure of a proportional valve with dynamic compensation function of the present invention.

[0026] Figure 8 yes Figure 7 A partial enlarged view of point D.

[0027] Figure 9 It is a three-dimensional exploded view of an active valve core and a passive valve core in a proportional valve with a dynamic compensation function of the present invention.

[0028] Figure 10 It is a three-dimensional exploded view of a pressure trigger component in a proportional valve with dynamic compensation function of the present invention.

[0029] The numbers in the figure are: 1. Valve seat; 11. Separator seat; 111. Sealing ring; 12. Fixed cylinder; 121. Connecting ring with hole; 13. Inlet; 14. Outlet; 2. Proportional solenoid; 21. Armature; 22. Rack; 31. Active valve core; 311. First flow port; 312. Connecting shaft; 313. Gear; 32. Passive valve core; 321. Second flow port; 322. Curved guide groove; 41. Pressure actuator; 411. Actuator ring; 412. Guide pin; 42. Pressure trigger assembly; 421. Pressure sensing cylinder; 4211. Pressure chamber; 4212. Back pressure chamber; 4213. Fixed ring; 422. Piston; 423. Return spring; 424. Maintaining spring; 425. Adjusting cylinder; 4251. Rotating ring; 43. Transmission rod. DETAILED DESCRIPTION

[0030] In order to further understand the features, technical means, specific objectives and functions achieved by the present invention, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0031] like Figure 1 、 Figure 2 、 Figure 3 and Figure 9 As shown, a proportional valve with dynamic compensation function includes a valve seat 1, a proportional electromagnet 2 arranged on the valve seat 1, a valve core assembly and a pressure regulating mechanism, the valve core assembly includes an active valve core 31 and a passive valve core 32 arranged coaxially, the active valve core 31 is transmission-connected to the armature 21 of the proportional electromagnet 2, and the passive valve core 32 can rotate relative to the active valve core 31; the active valve core 31 is provided with a first flow port 311, and the passive valve core 32 is provided with a second flow port 321, and the overlapping area of the first flow port 311 and the second flow port 321 constitutes a controlled throttling port; the pressure regulating mechanism includes: a pressure actuator 41, which is arranged in the valve seat 1 and close to the inlet 13 of the valve seat 1, and the pressure actuator 41 is transmission-connected to the passive valve core 32; the pressure The trigger assembly 42 is arranged in the valve seat 1 and close to the outlet 14 of the valve seat 1; the transmission rod 43 has its two ends connected to the pressure actuator assembly 41 and the pressure trigger assembly 42 respectively; when the pressure at the outlet 14 of the valve seat 1 is lower than the set value, the pressure trigger assembly 42 drives the pressure actuator assembly 41 through the transmission rod 43 to drive the passive valve core 32 to rotate in the direction of increasing the throttle opening; when the pressure at the outlet 14 of the valve seat 1 is higher than the set value, the pressure trigger assembly 42 drives the pressure actuator assembly 41 through the transmission rod 43 to drive the passive valve core 32 to rotate in the direction of reducing the throttle opening.

[0032] The valve core assembly comprises a coaxially arranged active valve core 31 and passive valve core 32. The active valve core 31 is connected to the proportional solenoid 2 via the armature 21, enabling direct control of its rotation angle. The passive valve core 32 can rotate relative to the active valve core 31, enabling coordinated adjustment. Both surfaces are provided with a first flow port 311 and a second flow port 321, respectively. These two ports overlap in space, forming a throttle. The opening of this throttle changes in real time based on the relative angle between the active and passive valve cores 31 and 32.

[0033] To further enhance its responsiveness to pressure fluctuations, the proportional valve is also equipped with a pressure regulating mechanism that responds to changes in outlet 14 pressure. This mechanism comprises a pressure actuator 41 positioned near the inlet 13 of the valve seat 1, a pressure trigger assembly 42 positioned near the outlet 14, and a transmission rod 43 connecting the two. The pressure trigger assembly 42 senses changes in outlet 14 pressure. When the outlet 14 pressure falls below a certain threshold, the transmission rod 43 drives the pressure actuator 41, causing the passive valve core 32 to rotate in a direction that increases the throttle opening. When the outlet 14 pressure exceeds the threshold, the same transmission mechanism causes the passive valve core 32 to rotate in the opposite direction, decreasing the throttle opening.

[0034] This structural design allows the active spool 31 to control the target opening, while the passive spool 32 dynamically adjusts the opening based on actual pressure feedback. The two work together to ensure that the throttle opening is controlled not only by electromagnetic signals but also by real-time compensation based on internal system pressure changes. This structure significantly improves the proportional valve's adaptability to environmental disturbances and reduces the impact of temperature and power supply fluctuations on control accuracy, thereby effectively enhancing system stability, response speed, and overall control quality.

[0035] like Figure 6 As shown, a separator seat 11 is provided in the valve seat 1, which separates the inner cavity of the valve seat 1 into an upstream cavity close to the inlet 13 and a downstream cavity close to the outlet 14; the active valve core 31 is rotatably supported on the end surface of the separator seat 11 close to the downstream cavity; the passive valve core 32 is rotatably supported on the end surface of the separator seat 11 close to the upstream cavity; the transmission rod 43 slides axially through the separator seat 11.

[0036] The separator seat 11 divides the inner cavity of the valve seat 1 into an upstream cavity near the fluid inlet 13 and a downstream cavity near the outlet 14, thereby forming a front-to-back structural partition. The valve core assembly includes an active valve core 31 and a passive valve core 32, both of which are coaxially arranged along the axis. The active valve core 31 is rotatably supported on the end surface of the separator seat 11 near the downstream cavity and is connected to the proportional solenoid 2 via the armature 21 to achieve controlled angle adjustment. The passive valve core 32 is rotatably supported on the end surface of the separator seat 11 near the upstream cavity and can rotate relative to the active valve core 31.

[0037] like Figure 4 and Figure 5 As shown, the pressure trigger assembly 42 includes: a pressure-sensitive cylinder 421, which is arranged in the downstream cavity; a piston 422, which is slidably arranged in the pressure-sensitive cylinder 421, dividing the inner cavity of the pressure-sensitive cylinder 421 into a pressure cavity 4211 and a back-pressure cavity 4212, and the pressure cavity 4211 is connected to the outlet 14 of the valve seat 1; a reset spring 423, which is arranged in the back-pressure cavity 4212, and is used to provide a reset force for the piston 422; the piston 422 is fixedly connected to the transmission rod 43, and when the pressure at the outlet 14 changes, the piston 422 displaces axially and drives the transmission rod 43 to slide, and then drives the passive valve core 32 to rotate through the pressure execution assembly 41.

[0038] The pressure trigger assembly 42 consists of a pressure-sensing cylinder 421, a piston 422 slidably disposed within the cylinder 421, a return spring 423, and a transmission rod 43 fixedly connected to the piston 422. The piston 422 divides the interior of the pressure-sensing cylinder 421 into a pressure chamber 4211 and a back-pressure chamber 4212. The pressure chamber 4211 is directly connected to the outlet 14 of the valve seat 1 and is used to sense changes in pressure at the outlet 14. A return spring 423 is disposed within the back-pressure chamber 4212 to provide a return force for the piston 422.

[0039] When the pressure at outlet 14 fluctuates, the pressure change within pressure chamber 4211 drives piston 422 to slide axially, thereby causing transmission rod 43 to slide as well. The movement of transmission rod 43 drives pressure actuator 41, which in turn acts on passive valve core 32, causing it to adjust its rotation angle and thereby change the throttle opening. When the pressure at outlet 14 falls below the set value, pressure trigger assembly 42 guides the passive valve core 32 to rotate, thereby increasing the throttle opening. When the pressure at outlet 14 exceeds the set value, pressure trigger assembly 42 causes the passive valve core 32 to rotate, thereby increasing the throttle opening.

[0040] The advantage of this structural design is that the pressure trigger assembly 42, through the collaboration of the pressure-sensing cylinder 421 and the piston 422, can reflect changes in outlet 14 pressure in real time and adjust the position of the passive valve core 32 through a precise transmission mechanism. Combined with the electronically controlled adjustment of the active valve core 31, the valve body can maintain stable flow control despite pressure fluctuations, while also reducing the electrical control system's sensitivity to environmental disturbances (such as voltage and current fluctuations, and temperature changes), thereby effectively improving the system's dynamic response capability and long-term operational stability.

[0041] like Figure 6 and Figure 8As shown, the pressure actuator assembly 41 includes an actuator ring 411 slidably arranged in the upstream cavity, the actuator ring 411 is connected to the transmission rod 43, the inner periphery of the actuator ring 411 is provided with a guide pin 412 extending along its radial direction, the surface of the passive valve core 32 is provided with a curved guide groove 322, the guide pin 412 extends into the curved guide groove 322 and slides with it, when the transmission rod 43 moves axially, the actuator ring 411 is driven to move axially along the transmission shaft, and the linear motion is converted into the rotational motion of the passive valve core 32 through the cooperation of the guide pin 412 and the curved guide groove 322.

[0042] When the pressure at the outlet 14 changes, the pressure in the pressure chamber 4211 pushes the piston 422 to slide axially, and the transmission rod 43 slides accordingly, converting the pressure change into mechanical displacement.

[0043] The transmission rod 43 passes through the partition seat 11 and is connected to the pressure actuator assembly 41 disposed in the upstream chamber. This assembly includes an actuator ring 411 slidably disposed within the upstream chamber. A plurality of radially extending guide pins 412 are arranged on the inner circumference of the actuator ring 411 and are fixedly connected to the transmission rod 43. The outer surface of the passive valve core 32 is provided with a curved guide groove 322 that cooperates with the guide pins 412. The guide pins 412 are embedded in the guide groove and slide therewith. When the actuator ring 411 undergoes axial displacement driven by the transmission rod 43, the guide pins 412 move along the curved guide groove 322, thereby converting the linear sliding movement of the transmission rod 43 into the rotational movement of the passive valve core 32.

[0044] This mechanism enables the valve core control to have a dual adjustment mechanism: on the one hand, the active valve core 31 is directly controlled by the proportional solenoid 2, which can realize the electronic control adjustment of the throttle opening; on the other hand, the passive valve core 32 is driven by the pressure change of the outlet 14 to realize the angle adaptive adjustment through the mechanism linkage between the piston 422, the transmission rod 43, the execution ring 41 and the curved guide groove 322.

[0045] like Figure 4 and Figure 5 As shown, the pressure trigger assembly 42 also includes a maintaining spring 424 arranged in the pressure chamber 4211. The maintaining spring 424 cooperates with the return spring 423 to keep the piston 422 in the middle position of the inner cavity of the pressure sensing cylinder 421 under the state of no pressure difference. When the pressure at the outlet 14 of the valve seat 1 decreases, the piston 422 moves toward the pressure chamber 4211 under the combined action of the elastic force of the return spring 423 and the pressure reduction in the pressure chamber 4211; when the pressure at the outlet 14 of the valve seat 1 increases, the piston 422 moves toward the back pressure chamber 4212 under the combined action of the elastic force of the maintaining spring 424 and the pressure increase in the pressure chamber 4211.

[0046] The retaining spring 424 and the return spring 423 work together to keep the piston 422 in the middle position of the piston chamber 422 when there is no pressure difference. When the pressure at the outlet 14 of the valve seat 1 decreases, the pressure in the pressure chamber 4211 decreases. The elastic force of the return spring 423 and the pressure in the pressure chamber 4211 work together to move the piston 422 toward the pressure chamber 4211. This, in turn, drives the pressure actuator 41 through the transmission rod 43 to adjust the rotation angle of the passive valve core 32. When the pressure at the outlet 14 increases, the pressure in the pressure chamber 4211 increases. The retaining spring 424 and the return spring 423 work together to move the piston 422 toward the back pressure chamber 4212, thereby adjusting the working state of the pressure actuator 41.

[0047] By incorporating a retaining spring 424, the pressure trigger assembly 42 ensures that the piston 422 remains in a stable position when no external pressure changes. This prevents repeated displacement caused by system pressure fluctuations and improves system stability and accuracy. Furthermore, the combined action of the pressure variations in the pressure chamber 4211 and back-pressure chamber 4212, along with the two springs, ensures smooth movement of the piston 422 and transmission rod 43. This allows for more precise and timely adjustment of the passive valve core 32 under conditions of significant pressure fluctuations.

[0048] like Figure 4 and Figure 5 As shown, the pressure trigger assembly 42 also includes an adjusting cylinder 425 threadedly connected to the inner wall of the valve seat 1, and the adjusting cylinder 425 includes: an operating end located outside the valve seat 1, for receiving a rotational driving force; a connecting end extending into the interior of the valve seat 1, forming an axially limited but relatively rotatable fitting relationship with the end of the pressure-sensing cylinder 421; when the adjusting cylinder 425 is rotated, the connecting end pushes the pressure-sensing cylinder 421 to move axially along the valve seat 1 to change the initial position of the piston 422.

[0049] The pressure trigger assembly 42 also includes an adjustment cylinder 425, which is threadedly connected to the inner wall of the valve seat 1 and consists of an externally operable rotating end and an internal connecting end connected to the pressure-sensing cylinder 421. When the adjustment cylinder 425 is rotated, the connecting end pushes the pressure-sensing cylinder 421 to move axially along the valve body. Although the two are structurally limited in axial direction, they retain the freedom of relative rotation. By adjusting the position of the pressure-sensing cylinder 421, the initial axial position of the piston 422 can be changed, thereby presetting the position of the transmission rod 43 and the actuator ring 411, causing the passive valve core 32 to deflect in the initial state of the system, thereby achieving manual adjustment of its initial rotation angle.

[0050] By rotating the adjustment cylinder 425, the valve's initial state is set, ensuring that the passive valve core 32 and the active valve core 31 are aligned or offset, further optimizing the throttle. This not only improves the system's adaptability and ease of commissioning, but also provides the ability to fine-tune and correct over time, effectively offsetting initial deviations caused by mechanical wear or temperature changes.

[0051] like Figure 4 and Figure 10 As shown, a fixing ring 4213 is provided at one end of the pressure-sensing cylinder 421 facing the outlet 14 of the valve seat 1 , and a rotating ring 4251 rotatably connected to the pressure-sensing ring is formed at one end of the regulating cylinder 425 facing the pressure-sensing cylinder 421 .

[0052] A fixing ring 4213 is provided on the end of the pressure-sensing cylinder 421 facing the outlet 14 of the valve seat 1 to limit the pressure-sensing cylinder 421 axially in the valve seat 1 to prevent it from axially dislodging while maintaining a flexible connection between it and the adjustment mechanism. The adjustment cylinder 425 is threadedly connected to the inner wall of the valve seat 1 and is divided into two ends:

[0053] One end is the operating end, located outside the valve body, which is convenient for users to apply rotational adjustment force;

[0054] The other end is a connecting end, which is provided with a rotating ring 4251 rotatably connected to the fixing ring 4213 of the pressure-sensing tube 421 to form a reliable rotation-force transmission interface.

[0055] This structure ensures that when the adjustment cylinder 425 rotates, its rotating ring 4251 converts the rotational motion into axial movement of the pressure-sensing cylinder 421, causing the entire pressure-sensing cylinder 421 to slide within the valve seat 1, thereby driving the piston 422 to pre-adjust its position axially. Because the pressure-sensing cylinder 421, fixed ring 4213, and rotating ring 4251 are connected in an axially limited but rotationally permitted manner, this connection ensures effective transmission of the rotational force of the adjustment cylinder 425 while preventing structural loosening or uncontrolled displacement.

[0056] like Figure 5 and Figure 10 As shown, a fixed cylinder 12 is also provided in the valve seat 1, and a chamber for installing the pressure-sensing cylinder 421 is formed between the outer wall of the fixed cylinder 12 and the inner wall of the valve seat 1, and a holed connecting ring 121 is provided between the inner end of the fixed cylinder 12 and the inner wall of the valve seat 1.

[0057] An annular mounting chamber is formed between the outer wall of the fixed cylinder 12 and the inner wall of the valve seat 1 for mounting and positioning the pressure-sensing cylinder 421. This design ensures a stable arrangement of the pressure-sensing cylinder 421 within the valve body, preventing it from loosening due to external pressure or operational deformation, while also facilitating its coordination with the adjustment cylinder 425, fixed ring 4213, rotating ring 4251, and other structures.

[0058] At the same time, the medium passing through the throttle port can enter the pressure chamber 4211 through the hole-carrying connecting ring 121 , thereby enabling the piston 422 to sense the pressure change of the outlet 14 .

[0059] like Figure 6 As shown, a sealing ring 111 is provided at the position where the transmission rod 43 passes through the partition seat 11 .

[0060] The sealing ring 111 is used to ensure that the pressure of the media in the upstream chamber and the downstream chamber will not be exchanged through the connection gap between the transmission rod 43 and the partition seat 11.

[0061] like Figure 7 As shown, a connecting shaft 312 is provided at one end of the active valve core 31 facing the outlet 14 of the valve seat 1 , and a gear 313 is provided on the connecting shaft 312 . The armature 21 of the proportional solenoid 2 extends into the valve seat 1 and is provided with a rack 22 , which meshes with the gear 313 .

[0062] When proportional solenoid 2 receives a data signal, its armature 21 extends axially, driving the rack 22 mounted on the armature 21 to produce linear displacement. During this movement, rack 22 engages with gear 313 on connecting shaft 312, causing gear 313 to undergo angular displacement about its axis. As gear 313 rotates, the active valve core 31 is driven by gear 313 to rotate and adjust, gradually changing the throttle opening and controlling the fluid flow.

[0063] The above embodiments merely represent one or more embodiments of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of protection of the present invention. It should be noted that a person of ordinary skill in the art may make various modifications and improvements without departing from the spirit of the present invention, and such modifications and improvements fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be subject to the appended claims.

Claims

1. A proportional valve with dynamic compensation function, comprising a valve seat and a proportional electromagnet arranged on the valve seat, characterized in that: Also includes valve core assembly and pressure regulating mechanism, The valve core assembly includes an active valve core and a passive valve core arranged coaxially. The active valve core is connected to the armature of the proportional solenoid through transmission, and the passive valve core can rotate relative to the active valve core. The active valve core is provided with a first flow port, the passive valve core is provided with a second flow port, and the overlapping area of the first flow port and the second flow port constitutes a controlled throttle port; The pressure regulating mechanism includes: A pressure actuator is arranged in the valve seat and close to the inlet of the valve seat, and the pressure actuator is in driving connection with the passive valve core; a pressure trigger assembly disposed in the valve seat and adjacent to an outlet of the valve seat; The transmission rod has two ends connected to the pressure actuator component and the pressure trigger component respectively; When the outlet pressure of the valve seat is lower than the set value, the pressure trigger assembly drives the pressure actuator assembly through the transmission rod to drive the passive valve core to rotate in the direction of increasing the throttle opening; when the outlet pressure of the valve seat is higher than the set value, the pressure trigger assembly drives the pressure actuator assembly through the transmission rod to drive the passive valve core to rotate in the direction of reducing the throttle opening.

2. A proportional valve with dynamic compensation function according to claim 1, characterized in that: A separator seat is provided in the valve seat, which divides the inner cavity of the valve seat into an upstream cavity close to the inlet and a downstream cavity close to the outlet; The active valve core is rotatably supported on the end surface of the separation seat close to the downstream cavity; The passive valve core is rotatably supported on the end surface of the separation seat close to the upstream cavity; The transmission rod slides axially and penetrates the partition seat.

3. A proportional valve with dynamic compensation function according to claim 2, characterized in that: The pressure-activated components include: a pressure-sensing cylinder, disposed in the downstream cavity; The piston is slidably disposed in the pressure-sensing cylinder to separate the inner cavity of the pressure-sensing cylinder into a pressure cavity and a back-pressure cavity, wherein the pressure cavity is communicated with the valve seat outlet; A return spring is provided in the back pressure chamber to provide a return force to the piston; The piston is fixedly connected to the transmission rod. When the outlet pressure changes, the piston moves axially and drives the transmission rod to slide, thereby driving the passive valve core to rotate through the pressure actuator.

4. A proportional valve with dynamic compensation function according to claim 3, characterized in that: The pressure actuator assembly includes an actuator ring slidably arranged in the upstream chamber, the actuator ring is connected to the transmission rod, the inner circumference of the actuator ring is provided with a guide pin extending radially thereof, the surface of the passive valve core is provided with a curved guide groove, the guide pin extends into the curved guide groove and slides with it, when the transmission rod moves axially, the actuator ring is driven to move axially along the transmission shaft, and the linear motion is converted into the rotational motion of the passive valve core through the cooperation of the guide pin and the curved guide groove.

5. A proportional valve with dynamic compensation function according to claim 3 or 4, characterized in that: The pressure trigger assembly also includes a maintaining spring arranged in the pressure chamber, which cooperates with the return spring to keep the piston in the middle position of the pressure sensing cylinder cavity when there is no pressure difference. When the valve seat outlet pressure decreases, the piston moves toward the pressure chamber under the combined action of the return spring force and the pressure reduction in the pressure chamber; When the pressure at the valve seat outlet increases, the piston moves toward the back pressure chamber under the combined action of the spring force and the pressure increase in the pressure chamber.

6. A proportional valve with dynamic compensation function according to claim 3 or 4, characterized in that: The pressure trigger assembly also includes an adjustment cylinder threadedly connected to the inner wall of the valve seat, and the adjustment cylinder includes: An operating end located outside the valve seat and configured to receive a rotational driving force; The connecting end extending into the interior of the valve seat forms an axially limited but relatively rotatable fitting relationship with the end of the pressure-sensing tube; When the regulating cylinder is rotated, the connecting end pushes the pressure-sensing cylinder to move axially along the valve seat to change the initial position of the piston.

7. The proportional valve with dynamic compensation function according to claim 6, characterized in that: A fixed ring is provided on one end of the pressure-sensing tube facing the valve seat outlet, and a rotating ring rotatably connected to the pressure-sensing ring is formed on one end of the regulating tube facing the pressure-sensing tube.

8. The proportional valve with dynamic compensation function according to claim 6, characterized in that: A fixed cylinder is also provided in the valve seat, and a chamber for installing a pressure-sensing cylinder is formed between the outer wall of the fixed cylinder and the inner wall of the valve seat. A connecting ring with a hole is provided between the inner end of the fixed cylinder and the inner wall of the valve seat.

9. A proportional valve with dynamic compensation function according to any one of claims 1 to 4, characterized in that: A sealing ring is provided at the position where the transmission rod passes through the partition seat.

10. A proportional valve with dynamic compensation function according to any one of claims 1 to 4, characterized in that: One end of the active valve core facing the valve seat outlet is provided with a connecting shaft, a gear is provided on the connecting shaft, the armature of the proportional electromagnet extends into the valve seat and is provided with a rack, and the rack is meshed with the gear.

Images