Spring attenuation self-compensation type proportional pressure valve

Abstract

The invention relates to the field of pressure valves, in particular to a spring attenuation self-compensation type proportional pressure valve. Comprising a valve body, a valve element and a main spring, the valve body is provided with an inlet flow channel and an outlet flow channel which are communicated with each other, a spring seat capable of axially moving is arranged in the valve body, the free end of the main spring abuts against the spring seat, the periphery of the spring seat is coaxially sleeved with an annular pressure bin, and a piston ring is arranged in the annular pressure bin in a sliding mode. The valve body is provided with a pressure guiding channel, one end of the pressure guiding channel is communicated with the outlet flow channel, the other end of the pressure guiding channel is communicated with the feedback pressure cavity, the pressure guiding channel is provided with a control valve, and the inlet flow channel is provided with a pressure sensor. Inlet pressure is monitored through the pressure sensor, the control valve is opened when the main spring is attenuated, outlet standby pressure is introduced to drive the piston ring to compress the main spring to form compensation pre-tightening force, impact and overcompensation are effectively restrained, accurate reset of opening pressure is ensured, and control precision and operation reliability are improved.

Description

Technical Field

[0001] This invention relates to the field of pressure valves, specifically to a spring-damped self-compensating proportional pressure valve. Background Technology

[0002] In existing air compressors or fluid systems, proportional pressure valves typically rely on the balance between spring preload and medium pressure to control the valve core's opening and closing, with the set pressure determined by the initial spring compression. However, springs are prone to elastic decay under long-term high temperatures, alternating loads, and corrosive environments, leading to a decrease in preload. This causes the valve to open prematurely at pressures lower than the set value, resulting in uncontrolled system pressure.

[0003] The currently published Chinese patent authorization announcement number CN115013573B discloses an air compressor pressure valve with precisely adjustable pressure. It includes an upper housing and a middle housing fixedly mounted on the bottom surface of the upper housing. A lower housing is fixedly mounted on the bottom surface of the middle housing, and a threaded vent sleeve is fixedly mounted on the bottom surface of the middle part of the lower housing. A driving assembly is installed at the upper end of the upper housing, and a sealing plate is embedded in the outer wall of one side of the lower end of the upper housing. An upper mounting groove is provided in the upper inner cavity of the upper housing, and a lower mounting groove is provided in the lower inner cavity of the upper housing. A spring assembly is provided in the inner cavity of the lower mounting groove, and a snap-fit ​​fixing assembly is provided in the inner cavity of one side of the lower end of the upper housing, located on one side of the spring assembly.

[0004] According to the aforementioned patent, abnormal exhaust is detected by pressure and gas flow sensors. When spring decay causes the pressure to fall below the set value and pressure is released, the motor drives the threaded column to move downward, compressing the spring to compensate for the preload and achieve automatic adjustment. However, the lack of limiting protection for the compensation amount means that continuous compression may lead to spring overload or valve core jamming, resulting in the loss of the safe pressure relief function.

[0005] Therefore, there is a need for a spring-attenuation self-compensating proportional pressure valve that automatically adjusts the spring preload based on real-time feedback of the inlet pressure, actively compensates for spring elastic decay rather than hysterically corrects it, and has an over-compensation protection mechanism to ensure that the compensation process does not cause the valve core to jam or lose its pressure relief function. Summary of the Invention

[0006] To address the problems existing in the prior art, a spring-damping self-compensating proportional pressure valve is provided. By monitoring the inlet pressure with a pressure sensor, the valve opens when the main spring weakens, introducing outlet backup pressure to drive the piston ring to compress the main spring and form a compensating preload. This effectively suppresses impact and overcompensation, ensures accurate reset of the opening pressure, and improves control accuracy and operational reliability.

[0007] To address the problems of existing technologies, this invention provides a spring-damped self-compensating proportional pressure valve, comprising a valve body, a valve core disposed therein, and a main spring for axially pressing the valve core. The valve body has an inlet flow channel and an outlet flow channel that are interconnected. The valve body has an axially movable spring seat, and the free end of the main spring abuts against the spring seat. An annular pressure chamber, fixedly connected to the valve body, is coaxially sleeved on the outer periphery of the spring seat. A piston ring that cooperates with the spring seat is slidably disposed within the annular pressure chamber, forming a feedback pressure chamber between the annular pressure chamber and the piston ring. The valve body has a pressure-inducing channel, one end of which is connected to the outlet flow channel, and the other end of which is connected to the feedback pressure chamber. During the pressurization process of the feedback pressure chamber, the piston ring is compressed, causing the spring seat to gradually squeeze the main spring, forming a compensating preload. The pressure-inducing channel is equipped with a control valve, and the inlet flow channel is equipped with a pressure sensor. When the pressure sensor detects that the inlet pressure is continuously higher than a set threshold, the control valve is in the open state; when the pressure sensor detects that the inlet pressure has fallen back to the normal range, the control valve is in the closed state.

[0008] Preferably, the end of the annular pressure chamber facing the valve core is an open end, the piston ring is provided with a pushing part extending outward through the open end of the annular pressure chamber, and the spring seat is provided with a step for the pushing part to abut.

[0009] Preferably, the inner and outer walls of the piston ring are tightly fitted to the inner surface of the annular pressure chamber, and the piston ring has a chamfered structure on the side facing the closed end of the annular pressure chamber. The annular pressure chamber has a branch port communicating with the pressure channel at the position corresponding to the chamfered structure.

[0010] Preferably, the inner side of the pusher is provided with a compression spring sleeved on the annular pressure chamber. One end of the compression spring is fixedly connected to the piston ring, and the other end is fixedly connected to the annular pressure chamber. When the feedback pressure chamber is pressurized and the piston ring is pressed and moved, the compression spring is in a compressed state.

[0011] Preferably, the spring seat is provided with a sliding part embedded in the inner wall of the annular pressure chamber, and a tension spring is fixedly connected between the sliding part and the valve body along the axial direction. When the spring seat moves towards the valve core under the action of the piston ring, the tension spring is in a stretched state.

[0012] Preferably, the valve body has a plurality of outlet channels communicating with the inlet channel along its circumference, and each outlet channel has a corresponding pressure-feeding channel communicating with the feedback pressure chamber.

[0013] Preferably, each pressure channel is provided with a control valve, the control valve including a guide sleeve fixedly disposed on the outside of the valve body and a valve shaft rotatably disposed in the guide sleeve, the valve shaft having a valve head at its downwardly extending end, the valve body having a groove for the valve head to be inserted at the position corresponding to the pressure channel, and the valve head having an interface that can communicate with the pressure channel.

[0014] Preferably, a limiting block is fixed on the valve shaft, and the guide sleeve has two sides that can abut against the limiting block. When the limiting block is rotated to abut against one side of the edge of the guide sleeve, the interface on the valve head and the pressure channel are in a connected or staggered state.

[0015] Preferably, a guide shaft is coaxially provided in the valve body. One end of the guide shaft is fixedly connected to the valve body, and the other end extends outward through the spring seat and the valve core to the inlet flow channel. The extended end of the guide shaft is provided with a secondary spring fixedly connected to the valve core. When the valve core opens the inlet flow channel, the main spring is compressed and the secondary spring is stretched at the same time, forming a cooperative bidirectional reset structure.

[0016] Preferably, the end of the guide shaft extending into the inlet flow channel is provided with a cone for guiding the airflow around the impact valve core end face of the auxiliary spring.

[0017] The advantages of this application compared to the prior art are: 1. This invention integrates a self-compensating mechanism based on outlet backup pressure feedback into a pressure valve. It uses a pressure sensor to monitor abnormal inlet pressure and automatically opens the pressure channel after determining that the main spring has weakened. This allows the outlet pressure to drive the piston ring to push the spring seat to compress the main spring, thus forming a compensating preload.

[0018] The compensation mechanism effectively offsets the loss of preload caused by fatigue, high temperature or corrosion of the main spring, so that the opening pressure is automatically restored to the set value without manual intervention. This improves the long-term stability, accuracy and reliability of pressure control, while avoiding the need for frequent maintenance or replacement of the main spring.

[0019] 2. This invention achieves precise and stable compensation for the attenuation of the main spring by constructing a multi-channel compensation mechanism within the valve body and combining the bidirectional elastic constraints of the compression spring and tension spring. The radial sealing and chamfered flow guiding design between the piston ring and the annular pressure chamber ensure efficient pressure transmission, and multiple circumferential pressure taps guarantee uniform pressure establishment within the chamber.

[0020] The pressure sensor monitors the inlet pressure in real time. When it detects that the pressure is consistently higher than the set threshold, it determines that the main spring performance has degraded and outputs a signal to control the control valve in the pressure tapping channel to open, ensuring that the outlet backup pressure is only conducted to the feedback pressure chamber when needed. This effectively suppresses shocks and overcompensation, improving the control accuracy, reset reliability, and adaptability of the pressure valve during long-term operation.

[0021] 3. This invention constructs a bidirectional reset structure in which the main spring and the secondary spring work together by setting a tapered head at the end of the guide shaft and configuring a secondary spring between the valve core and the guide shaft. When the valve core is opened, the main spring is compressed and the secondary spring is stretched, forming an elastic constraint in opposite directions. This not only improves the stability and reset accuracy of the valve core movement, but also effectively compensates for the performance loss of the main spring after it decays.

[0022] Meanwhile, the cone-shaped head blocks and diverts the inlet airflow, guiding the gas to flow smoothly around its outer circumference, preventing high-speed airflow from directly impacting the secondary spring and thus preventing performance degradation due to vibration, fatigue, or deformation. This ensures normal opening and closing response of the valve core while enhancing the durability and long-term operational reliability of both the main and secondary springs. Attached Figure Description

[0023] Figure 1 This is a three-dimensional structural diagram of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0024] Figure 2 This is a partial three-dimensional structural cross-sectional view of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0025] Figure 3 This is a planar sectional view of the valve core, spring seat, and main spring of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0026] Figure 4 This is a three-dimensional structural cross-sectional view of the valve core, spring seat, and main spring of a spring-attenuated self-compensating proportional pressure valve according to the present invention.

[0027] Figure 5 This is the invention Figure 3 Enlarged diagram of point A.

[0028] Figure 6 This is the invention Figure 3 Enlarged diagram of point B.

[0029] Figure 7 This is a three-dimensional structural cross-sectional view of the outlet flow channel and pressure tapping channel of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0030] Figure 8 This is a three-dimensional structural cross-sectional view of the annular pressure chamber and pressure tapping channel of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0031] Figure 9 This is a partial three-dimensional structural diagram of one side of the valve body outlet flow channel of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0032] Figure 10 This is a partial three-dimensional structural cross-sectional view of one side of the outlet flow channel of a spring-damped self-compensating proportional pressure valve according to the present invention.

[0033] The following are the labels in the diagram: 1. Valve body; 11. Inlet flow channel; 12. Outlet flow channel; 121. Pressure tapping channel; 13. Guide shaft; 131. Secondary spring; 132. Cone head; 2. Valve core; 3. Main spring; 4. Spring seat; 41. Step; 42. Sliding part; 43. Tension spring; 5. Annular pressure chamber; 51. Feedback pressure chamber; 511. Branch port; 6. Piston ring; 61. Pushing part; 62. Compression spring; 7. Control valve; 71. Guide sleeve; 711. Fixed magnet; 72. Valve shaft; 721. Movable magnet; 722. Throttle; 73. Valve head; 731. Interface; 8. Pressure sensor. Detailed Implementation

[0034] To further understand the features, technical means, and specific objectives and functions achieved by the present invention, the present invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.

[0035] See Figures 1-5 As shown, a spring-damped self-compensating proportional pressure valve includes a valve body 1, a valve core 2 disposed therein, and a main spring 3 for axially pressing against the valve core 2. The valve body 1 has an inlet flow channel 11 and an outlet flow channel 12 that are interconnected. An axially movable spring seat 4 is provided inside the valve body 1. The free end of the main spring 3 abuts against the spring seat 4. An annular pressure chamber 5, fixedly connected to the valve body 1, is coaxially sleeved on the outer periphery of the spring seat 4. A piston ring 6, which cooperates with the spring seat 4, is slidably disposed within the annular pressure chamber 5. A feedback pressure chamber 51 is formed between the annular pressure chamber 5 and the piston ring 6. The valve body 1 is provided with a pressure channel 121. One end of the pressure channel 121 is connected to the outlet flow channel 12, and the other end is connected to the feedback pressure chamber 51. During the pressurization process of the feedback pressure chamber 51, the piston ring 6 is pressed and drives the spring seat 4 to gradually squeeze the main spring 3, forming a compensating preload. The pressure channel 121 is provided with a control valve 7, and the inlet flow channel 11 is provided with a pressure sensor 8. When the pressure sensor 8 detects that the inlet pressure is continuously higher than the set threshold, the control valve 7 is in the open state. When the pressure sensor 8 detects that the inlet pressure has fallen back to the normal range, the control valve 7 is in the closed state.

[0036] Under normal operating conditions, the valve core 2 is axially pressed by the main spring 3, sealing the inlet flow channel 11 and preventing gas from passing through. At this time, the control valve 7 in the pressure channel 121 is in the closed state, the feedback pressure chamber 51 is completely isolated from the outlet flow channel 12, there is no additional pressure in the chamber, the piston ring 6 is stationary, the spring seat 4 remains in the initial position, and the main spring 3 maintains its original pre-compression.

[0037] During the process of gas entering the inlet channel 11, the valve core 2 is pushed open under the set pressure. At this time, the main spring 3 is compressed, and the inlet channel 11 is connected to the outlet channel 12. The entire pressure valve operates stably according to the set opening pressure.

[0038] As the pressure valve operates for an extended period, the main spring 3 gradually loses its elasticity due to factors such as fatigue, high temperature, or environmental corrosion, resulting in a decrease in its stiffness or effective preload. This causes the valve core 2 to open prematurely before the system pressure reaches the original set value, preventing the system from building up sufficient pressure. To compensate for this deficiency, the gas supply system continuously increases the pressure in an attempt to reach the target value, thus causing the actual pressure in the inlet flow channel 11 to remain higher than the normal set threshold for an extended period.

[0039] Because the inlet flow channel 11 releases prematurely, the system pressure remains confined to a low level. Meanwhile, the continuous air supply and localized flow resistance cause pressure buildup in the inlet flow channel 11, resulting in an abnormally high inlet pressure that is above the normal steady state but below the target value for an extended period. This state is identified by the pressure sensor 8 as continuously exceeding a preset diagnostic threshold, thus serving as the basis for judging the attenuation of the main spring 3 and triggering subsequent self-compensation actions.

[0040] When the inlet pressure is detected to not only exceed the set threshold but also remain at a high level for a period of time, the control system determines that this is due to the performance degradation of the main spring 3, rather than a momentary fluctuation, and immediately issues a command to open the control valve 7 in the pressure tapping channel 121. After the control valve 7 opens, the current system pressure in the outlet flow channel 12, i.e., the backup pressure, is introduced into the feedback pressure chamber 51 through the pressure tapping channel 121. As compressed air continues to enter, the pressure in the feedback pressure chamber 51 gradually increases. This pressure acts on the side of the piston ring 6 facing the closed end of the chamber, pushing the piston ring 6 to move axially toward the valve core 2.

[0041] Because of the mating relationship between the piston ring 6 and the spring seat 4, the axial displacement of the piston ring 6 is synchronously transmitted to the spring seat 4, forcing the spring seat 4 to move as a whole towards the valve core 2. This movement of the spring seat 4 further compresses the main spring 3, causing it to generate a greater reaction force. This additional compression driven by external pressure forms a compensation for the original preload, i.e., a compensating preload.

[0042] As the preload of the main spring 3 increases, the valve core 2 requires a higher medium thrust to overcome the spring force and open, causing the actual opening pressure of the inlet flow channel 11 to gradually rise back to the set value. The system pressure thus stabilizes, and the pressure in the inlet flow channel 11 also drops. Once the inlet pressure drops to the normal range and remains stable, the control valve 7 is immediately closed. After the control valve 7 is closed, the pressure tapping channel 121 is cut off, and the feedback pressure chamber 51 no longer receives new pressure input. The pressure inside the chamber keeps the piston ring 6 in the pressurized position, thus fixing the position of the spring seat 4, and the compensation action remains in the current state. Thus, the entire self-compensation process is completed without manual intervention. It automatically adjusts the preload of the main spring 3 by detecting abnormal inlet pressure and using the outlet backup pressure as a power source, maintaining the accuracy and stability of the pressure valve's opening pressure even when the performance of the main spring 3 deteriorates.

[0043] See Figures 3-5 As shown, the end of the annular pressure chamber 5 facing the valve core 2 is an open end, the piston ring 6 is provided with a pushing part 61 extending outward through the open end of the annular pressure chamber 5, and the spring seat 4 is provided with a step 41 for the pushing part 61 to abut.

[0044] When the feedback pressure chamber 51 is filled with pressure medium, the piston ring 6 moves axially toward the valve core 2 under the pressure inside the chamber, and its pushing part 61 passes through the opening end of the annular pressure chamber 5 and extends outward. The front end of the pushing part 61 abuts against the step 41 surface provided on the spring seat 4, thereby directly transmitting the axial thrust of the piston ring 6 to the spring seat 4.

[0045] Under continuous pressure, the pusher 61 continuously applies force to the step 41, forcing the spring seat 4 to move synchronously towards the valve core 2, thereby compressing the main spring 3 and achieving dynamic compensation of the preload. This ensures reliable force transmission between the piston ring 6 and the spring seat 4, guaranteeing the smoothness and accuracy of the compensation action.

[0046] See Figures 3-5 As shown, the inner and outer walls of the piston ring 6 are tightly fitted to the inner surface of the annular pressure chamber 5. The piston ring 6 has a chamfered structure on the side facing the closed end of the annular pressure chamber 5. The annular pressure chamber 5 has a branch port 511 connected to the pressure channel 121 at the position corresponding to the chamfered structure.

[0047] The inner and outer walls of the piston ring 6 are tightly fitted to the inner surface of the annular pressure chamber 5, forming a good radial seal and ensuring that the pressure medium in the feedback pressure chamber 51 will not leak along the circumference of the piston ring 6 during the pressurization process.

[0048] When the pressure channel 121 is open, the outlet backup pressure enters the annular pressure chamber 5 through the branch port 511. Since the piston ring 6 has a chamfered structure on the side facing the closed end, the pressure medium can flow smoothly into the chamber on the back side of the piston ring 6, i.e., the feedback pressure chamber 51, through the branch port 511. As the pressure accumulates in the chamber behind the chamfered structure, the effective pressure-bearing area acting on the closed end side of the piston ring 6 gradually increases, thereby stably pushing the piston ring 6 to move axially towards the valve core 2, providing reliable power for the subsequent drive spring seat 4 to compress the main spring 3.

[0049] See Figures 3-5 and Figure 8 As shown, the inner side of the push part 61 is provided with a compression spring 62 sleeved on the annular pressure chamber 5. One end of the compression spring 62 is fixedly connected to the piston ring 6, and the other end is fixedly connected to the annular pressure chamber 5. When the feedback pressure chamber 51 is pressurized and the piston ring 6 is pressed and moved, the compression spring 62 is in a compressed state.

[0050] In the initial state, the feedback pressure chamber 51 is not pressurized, the piston ring 6 is in the reset position, and the compression spring 62 is in its natural length or pre-tightened state. When the pressure channel 121 is opened and the outlet pressure enters the feedback pressure chamber 51, the pressure inside the chamber acts on the closed end of the piston ring 6, pushing the piston ring 6 to move axially toward the valve core 2, which in turn drives the pushing part 61 on it to move forward synchronously.

[0051] Meanwhile, as one end of the compression spring 62 moves with the piston ring 6 while the other end is fixed to the annular pressure chamber 5, the compression spring 62 is compressed, generating an elastic restoring force opposite to the direction of piston ring 6 movement. This restoring force serves two purposes: firstly, it buffers and stabilizes the displacement of the piston ring 6, preventing impacts or oscillations caused by sudden pressure changes; secondly, it assists the piston ring 6 in returning to its original position after the feedback pressure chamber 51 is depressurized, ensuring reliable system reset in uncompensated conditions.

[0052] See Figures 3-5 and Figure 8 As shown, the spring seat 4 is provided with a sliding part 42 embedded in the inner wall of the annular pressure chamber 5. A tension spring 43 is fixedly connected between the sliding part 42 and the valve body 1 along the axial direction. When the spring seat 4 moves towards the valve core 2 under the action of the piston ring 6, the tension spring 43 is in a stretched state.

[0053] In the initial state, the tension spring 43 is at its natural length, maintaining the initial position of the spring seat 4. When the feedback pressure chamber 51 is pressurized, the piston ring 6 is pressed and pushes the spring seat 4 towards the valve core 2, causing the sliding part 42 to move synchronously, thereby lengthening the tension spring 43 and putting it into the tension state.

[0054] The reverse tension generated by the tension spring 43 acts as a damper and limiter on the movement of the spring seat 4, preventing the valve core 2 from jamming due to excessive compression of the main spring 3. On the other hand, after the compensation is completed and the feedback pressure chamber 51 is depressurized, it can assist the spring seat 4 to return to the initial position, ensuring that the pressure valve restores the original set pressure under normal working conditions, and improving the system reset reliability and action consistency.

[0055] See Figure 5 , Figure 9 and Figure 10 As shown, the valve body 1 has several outlet channels 12 that communicate with the inlet channel 11 along its circumference, and each outlet channel 12 has a corresponding pressure channel 121 that communicates with the feedback pressure chamber 51.

[0056] When the pressure valve opens and gas enters each outlet channel 12 from the inlet channel 11 through the valve core 2, the backup pressure in each outlet channel 12 is simultaneously introduced into the feedback pressure chamber 51 through each pressure tapping channel 121. Since the multiple pressure tapping channels 121 are circumferentially distributed, the pressure medium can be evenly injected into the feedback pressure chamber 51 from multiple directions, so that the pressure in the chamber is quickly established and evenly distributed, thereby driving the piston ring 6 to move smoothly axially and avoiding uneven load or jamming caused by pressure entering from one side.

[0057] This multi-channel pressure-feeding structure not only improves the response speed and stability of pressure feedback, but also enhances the adaptability and reliability of the entire self-compensating mechanism under different working conditions.

[0058] See Figure 6 , Figure 7 , Figure 9 and Figure 10 As shown, each pressure channel 121 is provided with a control valve 7. The control valve 7 includes a guide sleeve 71 fixedly disposed on the outside of the valve body 1 and a valve shaft 72 rotatably disposed in the guide sleeve 71. The valve shaft 72 is provided with a valve head 73 at the downwardly extending end. The valve body 1 is provided with a groove for the valve head 73 to be inserted at the position corresponding to the pressure channel 121. The valve head 73 is provided with an interface 731 that can communicate with the pressure channel 121.

[0059] When the valve shaft 72 rotates to a specific angle, the interface 731 on the valve head 73 is aligned with the pressure channel 121, so that the outlet flow channel 12 is connected to the feedback pressure chamber 51, thereby realizing pressure introduction.

[0060] When the valve shaft 72 rotates to another angle, the valve head 73 closes the inlet of the pressure tapping channel 121, cutting off the flow path. By rotating the valve shaft 72, the valve head 73 is controlled to switch between the open and closed positions, thereby precisely controlling the on / off state of each pressure tapping channel 121, ensuring that the feedback pressure chamber 51 only receives the outlet backup pressure when compensation is needed, thus improving the accuracy and safety of the system response.

[0061] See Figure 6 , Figure 7 and Figure 9 As shown, a limiting block is fixed on the valve shaft 72, and the guide sleeve 71 has two sides that can abut against the limiting block. When the limiting block is rotated to abut against one side of the edge of the guide sleeve 71, the interface 731 on the valve head 73 is in a connected or staggered state with the pressure channel 121.

[0062] A fixed magnet 711 is fixedly connected to the guide sleeve 71, and the limiting block is a movable magnet 721.

[0063] Manual control: The valve body 1 is equipped with an alarm system electrically connected to the pressure sensor 8. The end of the valve shaft 72 extending outward is equipped with a handle 722 that can be gripped and rotated by the operator.

[0064] When the movable magnet 721 rotates to attract the fixed magnet 711, the interface 731 on the valve head 73 and the pressure channel 121 are in a coaxial communication state.

[0065] Electric control: The fixed magnet 711 and the movable magnet 721 are electromagnets, forming an electromagnetic drive system that is electrically connected to the pressure sensor 8.

[0066] When the movable magnet 721 rotates to attract the fixed magnet 711, the interface 731 on the valve head 73 and the pressure channel 121 are in a coaxial communication state.

[0067] See Figure 7 , Figure 8 and Figure 10 As shown, a guide shaft 13 is coaxially arranged inside the valve body 1. One end of the guide shaft 13 is fixedly connected to the valve body 1, and the other end extends outward through the spring seat 4 and the valve core 2 to the inlet flow channel 11. The extended end of the guide shaft 13 is provided with a secondary spring 131 fixedly connected to the valve core 2. When the valve core 2 opens the inlet flow channel 11, the main spring 3 is compressed, and at the same time the secondary spring 131 is stretched, forming a cooperative bidirectional reset structure.

[0068] When the system pressure rises to the set value, the thrust of the medium acting on the end face of the valve core 2 overcomes the preload of the main spring 3, pushing the valve core 2 to open axially along the guide shaft 13, thus connecting the inlet flow channel 11 with the outlet flow channel 12. During this opening process, the main spring 3 is compressed due to the movement of the valve core 2, and at the same time, the valve core 2 drives the auxiliary spring 131 to move together, causing the end of the auxiliary spring 131 to be stretched relative to the fixed guide shaft 13.

[0069] Therefore, the main spring 3 provides the reset clamping force, while the auxiliary spring 131 provides the tensile return force. During the movement of the valve core 2, the two form a bidirectional elastic constraint with opposite directions and synergistic action, constituting a synergistic bidirectional reset structure. This not only effectively maintains the stability and reset accuracy of the valve core 2's movement through the synergistic action of the auxiliary spring 131 after the performance of the main spring 3 degrades, but also accelerates the return of the valve core 2 when the pressure drops, improving dynamic response characteristics.

[0070] See Figure 7 and Figure 10 As shown, the end of the guide shaft 13 extending into the inlet flow channel 11 is provided with a cone 132 for guiding the airflow around the secondary spring 131 to impact the end face of the valve core 2.

[0071] When compressed gas enters from the inlet channel 11 and flows to the valve core 2, the cone 132 blocks and diverts the airflow entering the inlet channel 11 through its protruding streamlined structure, so that the mainstream gas flows smoothly around the outer circumference of the cone 132, thereby effectively preventing the high-speed airflow from directly impacting the auxiliary spring 131.

[0072] If the auxiliary spring 131 is subjected to direct impact from turbulent or high-speed airflow for a long period of time, it is prone to vibration, fatigue, or even deformation, which will affect its tensile properties and reset accuracy. The presence of the cone head 132 forms a pneumatic barrier, which protects the auxiliary spring 131 from airflow disturbance while ensuring that the valve core 2 is opened normally, thus ensuring the long-term stability and reliability of the cooperative bidirectional reset structure.

[0073] This invention monitors the inlet pressure in real time using a pressure sensor 8. Once it is determined that the preload has decreased due to fatigue, high temperature, or corrosion of the main spring 3, the control valve 7 is opened to introduce outlet backup pressure to drive the piston ring 6 to push the spring seat 4 to compress the main spring 3, forming a compensating preload, so that the opening pressure is automatically restored to the set value.

[0074] Multi-path circumferential pressure tapping ensures uniform and efficient pressure transmission. Compression spring 62 and tension spring 43 provide bidirectional elastic constraints, effectively suppressing impact, off-center loading, and overcompensation. Meanwhile, the auxiliary spring 131 can still work together to maintain the stability of valve core 2's movement and rapid reset capability after the main spring 3's performance degrades, improving the pressure control accuracy of the pressure valve.

[0075] The above embodiments only illustrate one or more implementations 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 those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A spring-damped self-compensating proportional pressure valve, comprising a valve body and a valve core disposed therein, and a main spring for axially pressing the valve core, wherein the valve body has an inlet flow channel and an outlet flow channel that are interconnected. Its features are, The valve body is provided with an axially movable spring seat, and the free end of the main spring abuts against the spring seat; The spring seat is coaxially sleeved with an annular pressure chamber that is fixedly connected to the valve body. A piston ring that cooperates with the spring seat is slidably disposed inside the annular pressure chamber, and a feedback pressure chamber is formed between the annular pressure chamber and the piston ring. The valve body is provided with a pressure-inducing channel, one end of which is connected to the outlet flow channel and the other end is connected to the feedback pressure chamber. During the pressurization process of the feedback pressure chamber, the piston ring is compressed, which causes the spring seat to gradually squeeze the main spring, forming a compensating preload force; The pressure channel is equipped with a control valve, and the inlet flow channel is equipped with a pressure sensor; When the pressure sensor detects that the inlet pressure is continuously higher than the set threshold, the control valve is in the open state; When the pressure sensor detects that the inlet pressure has dropped back to the normal range, the control valve is in the closed state.

2. The spring-damping self-compensating proportional pressure valve according to claim 1, characterized in that, The annular pressure chamber has an open end facing the valve core. The piston ring has a pushing part that extends outward through the open end of the annular pressure chamber. The spring seat has a step for the pushing part to abut.

3. The spring-damping self-compensating proportional pressure valve according to claim 2, characterized in that, Both the inner and outer walls of the piston ring are tightly fitted to the inner surface of the annular pressure chamber. The piston ring has a chamfered structure on the side facing the closed end of the annular pressure chamber. The annular pressure chamber has a branch port that communicates with the pressure channel at the position corresponding to the chamfered structure.

4. A spring-damping self-compensating proportional pressure valve according to claim 3, characterized in that, The inner side of the pusher is provided with a compression spring sleeved on the annular pressure chamber. One end of the compression spring is fixedly connected to the piston ring, and the other end is fixedly connected to the annular pressure chamber. When the feedback pressure chamber is pressurized and the piston ring is moved under pressure, the compression spring is in a compressed state.

5. A spring-damping self-compensating proportional pressure valve according to claim 4, characterized in that, The spring seat is provided with a sliding part embedded in the inner wall of the annular pressure chamber. A tension spring is fixedly connected to the sliding part and the valve body along the axial direction. When the spring seat moves towards the valve core under the action of the piston ring, the tension spring is in a stretched state.

6. A spring-damping self-compensating proportional pressure valve according to claim 1, characterized in that, The valve body has several outlet channels that communicate with the inlet channel along its circumference, and each outlet channel has a corresponding pressure-feeding channel that communicates with the feedback pressure chamber.

7. A spring-damping self-compensating proportional pressure valve according to claim 6, characterized in that, Each pressure channel is provided with a control valve, which includes a guide sleeve fixedly installed on the outside of the valve body and a valve shaft rotatably installed in the guide sleeve. The valve shaft has a valve head at its downwardly extending end. The valve body has a groove for the valve head to be inserted at the position corresponding to the pressure channel. The valve head has an interface that can communicate with the pressure channel.

8. A spring-damping self-compensating proportional pressure valve according to claim 7, characterized in that, A limiting block is fixed on the valve shaft, and the guide sleeve has two sides that can abut against the limiting block. When the limiting block is rotated to abut against one side of the edge of the guide sleeve, the interface on the valve head and the pressure channel are either connected or misaligned.

9. A spring-damping self-compensating proportional pressure valve according to claim 1, characterized in that, The valve body is coaxially provided with a guide shaft. One end of the guide shaft is fixedly connected to the valve body, and the other end passes through the spring seat and the valve core in sequence and extends outward to the inlet flow channel. The extended end of the guide shaft is provided with a secondary spring fixedly connected to the valve core. When the valve core opens the inlet flow channel, the main spring is compressed and the secondary spring is stretched at the same time, forming a cooperative bidirectional reset structure.

10. A spring-damping self-compensating proportional pressure valve according to claim 9, characterized in that, The end of the guide shaft extending into the inlet flow channel is provided with a cone to guide the airflow around the secondary spring and impact the valve core end face.

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