A fluid control system integrating a gate valve and a pressure reducing valve

Abstract

The present application relates to the field of valve structure, and particularly relates to a fluid control system integrating a gate valve and a pressure reducing valve. The control system comprises a pressure reducing valve, a gate valve, a pilot valve device and a gate separation device. The gate separation device synchronously blocks upstream fluid from entering the pilot valve device before adjusting the pilot valve device, which eliminates the risk of high pressure impact and establishes a zero pressure calibration environment. The pilot valve device of the present application serves as a pressure regulating center. The swing member thereof swings around a rotating shaft under the drive of fluid pressure, and synchronously drives the first plunger and the second plunger to move axially in opposite directions through double-sided connecting rods. When the high pressure fluid drives the first plunger to move into the flow guide cavity to open the high pressure port, the second plunger is synchronously opened to form a pressure relief channel. When the output pressure abnormally rises, the second plunger is reversely driven by the fluid to press the sealing surface, and the swing member is linked to lock the high pressure port. The diaphragm of the pressure reducing valve is driven to close the valve port, which realizes overpressure cut-off and dynamic pressure balance.

Description

Technical Field

[0001] The present invention relates to the field of valve structures, and in particular to a fluid control system integrating a gate valve and a pressure reducing valve. Background Art

[0002] In high-pressure fluid control systems, the pilot valve device of a traditional pressure reducing valve often faces the inherent defect of being out of sync with the pressure relief response and port closure when dealing with sudden pressure changes. Existing designs mostly rely on independent valve components or one-way feedback mechanisms. When the system pressure suddenly rises and requires emergency relief, the pressure relief channel opens slowly and there is a significant delay with the main valve port closure action, resulting in the inability to quickly release the control chamber pressure. At the same time, under overpressure conditions, the port seal closure cannot coordinate instantaneously, causing diaphragm feedback lag and insufficient valve port cut-off response. This not only causes the output pressure to oscillate repeatedly beyond the allowable range, but may also induce equipment damage or safety accidents due to the failure of overload protection, seriously restricting the system's dynamic stability and reliability in high-pressure differential and large-flow environments. Summary of the Invention

[0003] In view of the deficiencies raised in the above background technology, the present invention provides a fluid control system integrating a gate valve and a pressure reducing valve.

[0004] The present invention adopts the following technical solutions:

[0005] A fluid control system integrating a gate valve and a pressure reducing valve comprises a gate valve, a pressure reducing valve and a pilot valve device, wherein the gate valve is connected to an output port of the pressure reducing valve, the pilot valve device is connected to the pressure reducing valve, and the pilot valve device comprises:

[0006] A pilot valve body, wherein a flow guide cavity is formed inside the pilot valve body, and a high-pressure port and a low-pressure port are provided on the pilot valve body, wherein the high-pressure port is connected to the control cavity in the pressure reducing valve, and the low-pressure port is connected to the output end of the pressure reducing valve, and a first retaining ring is provided on the inner annular surface of the high-pressure port, and a second retaining ring is provided on the inner annular surface of the low-pressure port;

[0007] a swinging member, the swinging member being restricted from swinging in the guide cavity, an adjusting groove being provided in the middle of the swinging member, connecting rods being pivotally connected on both sides of the swinging member relative to the swing axis, the two connecting rods being pivotally connected to a first plunger and a second plunger respectively, the plug body of the first plunger being located in the high-pressure port, and the first plunger being located on a side of the first baffle ring facing the inside of the pilot valve body, the plug body of the second plunger being located in the low-pressure port, and the second plunger being located on a side of the second baffle ring facing the outside of the pilot valve body;

[0008] a transmission member, the transmission member being arranged in the guide cavity and being swingable, a rotating pin being fixed on one side of the transmission member, the rotating pin passing through the outside of the pilot valve body and fixing a push rod, one end of the transmission member being connected to a rotating wheel, the other end of the transmission member being connected to one end of a first spring, the other end of the first spring being connected to the pilot valve body, so that the elastic preload force of the first spring pulls the rotating wheel to swing upward with the rotating pin as the axis until it tops the adjusting groove;

[0009] an adjusting screw, the adjusting screw being spirally connected to the pilot valve body and abutting against the upper end of the push rod to block the elastic force of the first spring pulling the transmission member to swing;

[0010] When the high-pressure fluid in the control chamber of the pressure reducing valve overcomes the elastic force of the first spring and enters the guide chamber through the high-pressure port, the high-pressure fluid pushes the first plunger away from the first baffle ring and displaces toward the inside of the guide chamber, causing the swinging member to swing and driving the second plunger to leave the second baffle ring and displace toward the outside of the guide chamber, thereby opening the low-pressure port.

[0011] When the high-pressure fluid in the output end of the pressure reducing valve overcomes the elastic force of the first spring and enters the pilot valve body through the low-pressure port, the high-pressure fluid pushes the second plunger to press against the second baffle ring, causing the swinging member to swing and driving the first plunger to press against the first baffle ring to seal the high-pressure port.

[0012] In one possible implementation, the pilot valve body includes a shell and a cover, the internal space when the shell and the cover are closed forms the guide chamber, the high-pressure port and the low-pressure port are both arranged on the cover, the swing member and the transmission member are both arranged in the shell, and the adjusting screw is connected to the outside of the shell.

[0013] In one possible implementation, the cover body is screwed to fix a guide ring in the through holes corresponding to the high-pressure port and the low-pressure port, a guide hole is formed in the center of the guide ring, the first plunger and the second plunger both include a guide column and the plug body, the guide column and the connecting rod are pivotally connected, and the guide columns are respectively adapted to pass through the guide holes of the guide ring so that the plug body is located in the high-pressure port or the low-pressure port.

[0014] In a possible implementation, the pilot valve body is spirally connected to a first pipe member and a second pipe member, the high-pressure port is provided in the first pipe member, and the low-pressure port is provided in the second pipe member.

[0015] In a possible implementation, the pilot valve device further includes a protective cover adapted to be mounted outside the pilot valve body, and the protective cover covers the push rod and the adjusting screw.

[0016] In one possible implementation, the control system also includes a gate-off device, which is arranged on the gate valve. The gate-off device includes a split nut and a third spring and a fourth spring. Both sides of the valve body of the gate valve are connected to slidable split nuts, and the two split nuts are provided with a semicircular threaded groove on the side of the valve stem facing the gate valve. The two split nuts are connected to the valve body of the gate valve with a third spring, and the elastic force of the third spring pushes the thread grooves of the two split nuts to be spliced ​​toward the middle of the gate valve. After the thread grooves of the two split nuts are spliced, a complete threaded hole is formed. After the valve stem of the gate valve passes through the valve body of the gate valve, it is adapted to spirally pass through the two thread grooves to form a threaded hole. The fourth spring is connected between the valve plate of the gate valve and the inner wall of the valve body of the gate valve. The elastic force of the fourth spring pushes the valve plate to close the gate valve.

[0017] In one possible implementation, the gate release device also includes a turntable, which is restricted from rotating outside the valve body of the gate valve, and the valve stem passes through the center of the turntable. Two guide grooves are mirror-imaged on the side of the turntable facing the outside of the gate valve, and the path of the guide groove is an arc that is eccentric relative to the turntable; a guide pin is provided on the side of the split nut facing the gate valve, and the guide pins of the two split nuts are respectively embedded in the two guide grooves.

[0018] In one possible implementation, the pilot valve device further includes a protective cover, which is adapted to be mounted outside the pilot valve body and covers the push rod and the adjusting screw; a gear ring is fixed to the periphery of the turntable, and the protective cover fixes a rack, the rack and the gear ring are engaged, and when the protective cover is slid to open the pilot valve body, the rack is driven to move so that the gear ring rotates accordingly, driving the turntable to rotate, causing the two guide grooves to rotate and pushing the guide pin to move so that the two split nuts are separated.

[0019] In a possible implementation, a slider is fixed outside the valve body of the gate valve, a slide rail is fixed under the rack, and the slide rail is adapted to be embedded in the slider and slide.

[0020] In one possible implementation, the valve body of the gate valve is fixed with connecting seats on both sides of the valve stem, a guide rod is fixed between the two corresponding connecting seats, and guide holes are provided on both sides of the split nut. The guide holes are adapted to be fitted outside the guide rod, the third spring is sleeved outside the guide rod, and the two ends of the third spring respectively abut against the connecting seat and the split nut.

[0021] As can be seen from the above description of the structure of the present invention, compared with the prior art, the present invention has the following advantages: The pilot valve device of the present invention serves as the pressure regulation center of the pressure reducing valve. When the fluid pressure in the control chamber of the pressure reducing valve drives the first plunger into the guide chamber, it drives the swing member to swing. When the high-pressure fluid drives the first plunger into the guide chamber to open the high-pressure port, the second plunger is synchronously moved out of the guide chamber to open the low-pressure port, forming a pressure relief channel. The high-pressure fluid accumulated in the control chamber is quickly discharged to the external circuit through this pressure relief channel. The system pressure then drops below the second spring restoring force threshold. At this time, the valve disc reopens under the action of the pressure difference, allowing the pressure-regulated fluid to be stably discharged through the output port. When the discharge pressure increases abnormally, the fluid at the output port of the pressure reducing valve reversely drives the second plunger through the low-pressure port to press against the cover, forcibly closing the high-pressure port through the swing member. When the swing member swings in the opposite direction, the first plunger presses against the first retaining ring to close the high-pressure port, while the second plunger simultaneously presses against the second retaining ring to seal the low-pressure port. This action drives the diaphragm of the pressure reducing valve to close the valve port, achieving overpressure cutoff and dynamic pressure balance. It can be seen that the present invention can achieve dynamic balance and overload protection of the system working pressure, and is suitable for fluid pressure control under high pressure difference and large flow conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 It is a schematic diagram of the three-dimensional structure of the present invention.

[0023] Figure 2 It is a top view of the present invention.

[0024] Figure 3 For pressure reducing valve Figure 2 Schematic diagram of the cross-sectional structure in the AA direction.

[0025] Figure 4 For gate valve Figure 2 Schematic diagram of the cross-sectional structure in the middle BB direction.

[0026] Figure 5 It is a schematic diagram of the three-dimensional structure of the pilot valve device.

[0027] Figure 6 It is a schematic diagram of the cross-sectional structure of the pilot valve device.

[0028] Figure 7 for Figure 6 Enlarged schematic diagram at point C in the middle.

[0029] Figure 8 This is a schematic diagram of the three-dimensional structure of the pilot valve device after the pilot valve body is hidden.

[0030] Figure 9 This is a schematic diagram of the three-dimensional structure of the gate release device connecting the pilot valve device and the gate valve.

[0031] Figure 10 for Figure 9 Schematic diagram of the enlarged point D in the middle.

[0032] Figure 11 Schematic diagram of the valve cover end face of the gate valve connected to the turntable.

[0033] Figure 12 It is a schematic diagram of the three-dimensional structure of the split nut. DETAILED DESCRIPTION

[0034] In order to make the purpose, technical solutions and advantages of this application clearer, this application will be further described in detail below with reference to the accompanying drawings.

[0035] In the following, the terms "first," "second," etc. are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature specified as "first," "second," etc. may explicitly or implicitly include one or more of the features. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0036] In addition, in this application, directional terms such as "upper" and "lower" are defined relative to the orientation of the components in the drawings. It should be understood that these directional terms are relative concepts. They are used for relative description and clarification, and they can change accordingly according to changes in the orientation of the components in the drawings.

[0037] The present invention provides a fluid control system integrating a gate valve 2 and a pressure reducing valve 1, as shown in the attached figure. Figure 1 and 2 As shown, the control system includes a pressure reducing valve 1, a gate valve 2, a pilot valve device 3 and a gate release device 4. Among them, the gate valve 2 is connected to the output end 102 of the pressure reducing valve 1, the pilot valve device 3 is connected to the pressure reducing valve 1, and the gate release device 4 is connected to the gate valve 2.

[0038] The pressure reducing valve 1 adopts the pressure self-balancing structure design, and its structure is as shown in the attached Figure 3As shown, the internal cavity of the pressure reducing valve 1 is provided with a valve seat 11 to separate the input end 101 from the output end 102. The valve seat 11 is provided with a valve port 103 for controlling the flow of fluid between the input end 101 and the output end 102. A control chamber 104 is also provided at the end corresponding to the valve port 103 within the pressure reducing valve 1. The control chamber 104 and the internal cavity of the pressure reducing valve 1 are separated by a rubber diaphragm 12. The input end 101 of the pressure reducing valve 1 is connected to the control chamber 104 via a flow guide tube 16 to form a fluid passage. A rigid fixing plate is fixed in the middle of the diaphragm 12 to enhance structural stability. The side of the diaphragm 12 facing the valve port 103 is rigidly connected to the valve disc 15 via a connecting rod 14. The side of the diaphragm 12 facing the control chamber 104 is connected to a second spring 13. The tensile force of the second spring 13 acts on the diaphragm 12, causing it to move toward the valve port 103, thereby driving the valve disc 15 to press against the valve port 103 to form a seal. When fluid enters from the input end 101, the preload of the second spring 13 is overcome to lift the valve disc 15 to open the valve port 103, allowing the fluid to flow out steadily through the output end 102. At the same time, part of the fluid enters the control chamber 104 through the guide tube 16 to form feedback pressure.

[0039] As attached Figure 5 、 6 As shown in Figures 8 and 9, the pilot valve device 3 includes a pilot valve body 31, a swinging member 32, a transmission member 33, an adjusting screw 34, and a first spring 35. A flow guide chamber 301 is formed within the pilot valve body 31. The swinging member 32 and the transmission member 33 are both assembled within the flow guide chamber 301 to achieve dynamic adjustment of the fluid pressure. The pilot valve body 31 specifically includes a housing 311 and a cover 312. The cover 312 covers the opening of the housing 311 and is closed and fixed by bolts. The space formed therein is the flow guide chamber 301. The swinging member 32 and the transmission member 33 are both disposed within the housing 311, and the adjusting screw 34 is connected to the outside of the housing 311. A high-pressure port 313 and a low-pressure port 314 are respectively disposed on both sides of the surface of the cover 312. A first retaining ring 315 is disposed on the inner annular surface of the high-pressure port 313, and a second retaining ring 316 is disposed on the inner annular surface of the low-pressure port 314. The high-pressure port 313 is connected to the control chamber 104 in the pressure-reducing valve 1 via a high-pressure pipe, allowing high-pressure water in the control chamber 104 to flow into the diversion chamber 301 through the high-pressure port 313. The low-pressure port 314 is connected to the output end 102 of the pressure-reducing valve 1 via a high-pressure pipe, allowing the fluid in the diversion chamber 301 to flow to the output end 102 of the pressure-reducing valve 1 and then out.

[0040] Continue to refer to the attached Figure 5The cover 312 is screw-connected with a first pipe (not shown in the figure) and a second pipe (not shown in the figure), the high-pressure port 313 is a flow channel in the first pipe, and the low-pressure port 314 is a flow channel of the second pipe, so that the modular structure is formed, the high-pressure port 313 and the low-pressure port 314 can be independently formed with the respective pipes, the casting difficulty of the complex internal cavity structure of the cover 312 is reduced, the first blocking ring 315 and the second blocking ring 316 can be synchronously formed with annular sealing surfaces in the machining process of the first pipe and the second pipe respectively, and the selective replacement of a single port is facilitated during the later maintenance, and the production efficiency and the maintenance economy are both improved on the basis of ensuring the sealing reliability of the fluid channel.

[0041] With reference to the accompanying drawings Figure 6 and 8 The swing member 32 is limited to swing in the flow guide cavity 301. Specifically, a through shaft 321 is arranged in the middle of the swing member 32, bearings are assembled at both ends of the shaft 321, the bearings are fixed to the corresponding two sides of the shell 311, the shaft 321 is fixedly supported with the two sides of the shell 311, and the stability of the swing of the swing member 32 under the action of fluid pressure is ensured. An adjusting groove 322 is arranged in the middle of the swing member 32, and the groove opening of the adjusting groove 322 faces away from the cover 312. The two sides of the swing member 32 relative to the swing axis (i.e. the shaft 321) are both pivotally connected with connecting rods 323. In the embodiment, the pivoting can be formed by a through pin shaft, so that the two components pivotally connected with each other can swing relative to each other. The two connecting rods 323 are respectively pivotally connected with a first plunger 324 and a second plunger 325. The first plunger 324 and the second plunger 325 both include a guide column 326 and a plug body 327, wherein the guide column 326 is pivotally connected with the connecting rod 323, the plug body 327 of the first plunger 324 is located in the high-pressure port 313, and the plug body 327 of the first plunger 324 is located on the side of the first blocking ring 315 facing the inside of the valve body 31. The plug body 327 of the second plunger 325 is located in the low-pressure port 314, and the plug body 327 of the second plunger 325 is located on the side of the second blocking ring 316 facing the outside of the valve body 31. Further, the cover 312 is screw-fixed with a guide ring 38 in the through holes corresponding to the high-pressure port 313 and the low-pressure port 314, the center of the guide ring 38 forms a guide hole, and the guide column 326 is adapted to pass through the guide hole of the guide ring 38, so that the plug body 327 is located in the high-pressure port 313 or the low-pressure port 314, and the first plunger 324 and the second plunger 325 are both only allowed to move axially and linearly relative to the guide column 326 by the limitation of the guide hole.

[0042] When the fluid in the control chamber 104 enters the flow diversion chamber 301, the fluid pressure pushes the first plunger 324 into the flow diversion chamber 301, causing the first plunger 324 to disengage from the first baffle ring 315, thereby opening the high-pressure port 313 and driving the swing member 32 to swing. This in turn drives the second plunger 325 to move out of the flow diversion chamber 301 and disengage from the second baffle ring 316, thereby opening the low-pressure port 314. Conversely, when the fluid in the output end 102 enters the flow diversion chamber 301, the fluid pressure pushes the second plunger 325 into the flow diversion chamber 301, pressing against the second baffle ring 316 to seal the low-pressure port 314. This in turn drives the swing member 32 to swing in the opposite direction, causing the first plunger 324 to press against the first baffle ring 315 to close the high-pressure port 313. The lever structure of the swing member 32 linking the first and second plungers 324, 325 enables bidirectional control of the first and second plungers 324, 325. When the fluid pressure drives the swing member 32 to deflect around the rotating shaft 321, the lever principle synchronously decomposes the single rotational motion into axial reverse linear displacements of the first plunger 324 and the second plunger 325. That is, while one side of the swing member 32 presses down to push the first plunger 324 to move into the guide chamber 301 to open the high-pressure port 313, the other side pulls up to drive the second plunger 325 to move out of the guide chamber 301 to synchronously open the low-pressure port 314, ensuring that the displacement of the first plunger 324 and the second plunger 325 strictly follows the lever ratio relationship. Compared with the traditional single-axis driven rubber plug structure, it has an essential improvement, can eliminate the phase difference caused by the deformation of the elastic material, and realize the synchronization of the opening and closing actions of the high-pressure port 313 and the low-pressure port 314.

[0043] Please refer to the attached Figure 7 The centers of the first retaining ring 315 and the second retaining ring 316 are both tapered holes. The plug body 327 of the first plunger 324 is a cone that fits the center of the first retaining ring 315, and the plug body 327 of the second plunger 325 is a cone that fits the center of the second retaining ring 316. The matching structure of the tapered hole and the tapered plug body 327 allows the plug body 327 to automatically align along the centerline of the tapered hole during the tightening process, effectively compensating for coaxial deviations caused by valve body machining and assembly, and ensuring a 360° uniform fit of the sealing surface.

[0044] Continue to refer to the attached Figure 5 and 8, the transmission member 33 is fixed with a rotating pin 331 which penetrates the guide valve body 31 and is fixed with a push rod 332, and the structure design ensures that the transmission member 33 swings in the guide cavity 301 with the rotating pin 331 as the axis. As a preferred embodiment, the outer circumferential surface of the rotating pin 331 can be provided with an oil seal assembly, which effectively prevents fluid medium from leaking through the gap between the rotating pin 331 and the shell 311. One end of the transmission member 33 is configured with a rotating wheel 333, and the other end of the transmission member 33 is elastically connected with the cover 312 through a first spring 35. The first spring 35 can be a tension spring, and the two ends of the first spring 35 are respectively hooked with a connecting pin on the transmission member 33 and a connecting pin on the inner wall of the cover 312 to form reliable hooking. Under the pulling force formed by the elastic pre-tightening force of the first spring 35, the rotating wheel 333 swings upward around the rotating pin 331 and stably abuts against the adjusting inclined surface (for example, the left inclined surface) of the adjusting groove 322, so that the rotating wheel 333 pushes the swing member 32 to keep swinging to push the first plunger 324 towards the first blocking ring 315. Figure 6

[0045] The adjusting screw 34 is screw-connected with the guide valve body 31 through screw fitting, and the adjusting screw 34 abuts against the upper end side of the push rod 332 to offset the elastic force of the first spring 35 for swinging the transmission member 33. Specifically, when the adjusting screw 34 is screwed in along the low-pressure port 314 towards the high-pressure port 313, the adjusting screw 34 is axially displaced to push the push rod 332 to move, forcing the transmission member 33 to swing downward to drive the rotating wheel 333 to move downward, so that the adjusting inclined surface on the side of the adjusting groove 322 releases a larger swinging stroke space, and the first plunger 324 obtains a larger axial displacement under the action of fluid pressure. At this time, the tapered plug body 327 and the tapered hole form a wide annular flow channel, and the fluid passage is in a fully open state.

[0046] ​Conversely, when the adjusting screw 34 is rotated outward, causing the wheel 333 to move upward, the adjusting bevel compresses the effective stroke of the first plunger 324, limiting the depth to which the conical plug 327 can enter the tapered hole. This creates a narrow slit throttling effect through the interference fit between the conical surface and the tapered hole. In this state, when high-pressure fluid enters through the high-pressure port 313 and pushes the first plunger 324 downward, a wide annular flow channel is formed between the plug 327 and the tapered hole, and the fluid channel formed in the center of the first retaining ring 315 is open, thereby achieving maximum flow control of the system. Conversely, when the adjusting screw 34 is rotated outward in the opposite direction, the push rod 332 gradually releases its axial constraint, and the transmission member 33 swings toward the low-pressure port 314 under the contraction force of the first spring 35, driving the wheel 333 upward. The adjusting bevel compresses the effective stroke of the first plunger 324, limiting the depth to which the plug 327 can enter the tapered hole in the center of the retaining ring. At this point, when the first plunger 324 is pushed downward by the high-pressure fluid, a narrow slit is formed between the plunger body 327 and the tapered hole in the center of the retaining ring, thereby reducing the opening of the fluid channel formed by the first and second retaining rings 315 and 316, thereby achieving flow throttling. The above structure, through the synergistic effect of the adjusting screw 34 and the first spring 35, achieves stepless linear adjustment of the fluid channel opening, ensuring the stability and repeatability of the flow control process.

[0047] When the adjusting screw 34 is rotated inward, pushing the wheel 333 downward, the adjusting bevel frees up more swing travel space, allowing the first plunger 324 to achieve greater axial displacement under the action of fluid pressure. This creates a wide annular flow channel between the conical plug 327 and the tapered hole, placing the fluid channel in a fully open state. Conversely, when the adjusting screw 34 is rotated outward, causing the wheel 333 to move upward, the adjusting bevel compresses the effective travel of the first plunger 324, limiting the depth of the conical plug 327's entry into the tapered hole. This creates a narrow slit flow restriction through the interference fit between the conical surface and the tapered hole. The unique advantage of the conical seal pair lies in: when fluid pressure acts on the conical surface, a radial force component is generated, causing the contact pressure between the plug 327 and the hole wall to automatically increase with rising system pressure, achieving a dynamic, self-tightening seal. Furthermore, the self-centering nature of the conical surface ensures uniform sealing of the sealing strip at any opening, maintaining zero leakage reliability during linear flow regulation. This design achieves continuous, stepless control of the fluid channel's cross-sectional area through the precise coupling of mechanical displacement and conical surface geometry.

[0048] As attached Figure 9 As shown, the pilot valve device 3 also includes a protective cover 36, which is adapted to fit outside the pilot valve body 31 and covers the push rod 332 and the adjusting screw 34, thereby forming an effective protection for the adjusting screw 34 and the clearance between the rotating pin 331 and the housing 311, and avoiding accidental contact with the adjusting screw 34.

[0049] When the fluid pressure at the input end 101 of the pressure reducing valve 1 exceeds the preset threshold of the second spring 13 (i.e., the preload of the second spring 13), the high-pressure fluid enters the control chamber 104 through the flow conduit 16, generating pressure feedback. This pressure overcomes the elastic force of the second spring 13, driving the diaphragm 12 downward, causing the valve disc 15 to tightly close the valve port 103, achieving fluid shutoff. Simultaneously, the high-pressure fluid continues to flow toward the high-pressure port 313, overcoming the elastic constraint of the first spring 35, pushing the plug body 327 of the first plunger 324 away from the first retaining ring 315 and displacing it into the flow conduit chamber 301. The mechanical linkage of the swinging member 32 drives the plug body 327 of the second plunger 325 away from the second retaining ring 316 and displaced out of the flow conduit chamber 301, fully opening the low-pressure port 314 and forming a highly efficient pressure relief channel. The high-pressure fluid accumulated in the control chamber 104 is rapidly discharged to the external circuit through the pressure relief channel, and the system pressure is then reduced to below the restoring force threshold of the second spring 13. At this time, the valve flap 15 reopens under the action of the pressure difference, allowing the pressure-regulated fluid to be stably discharged through the output end 102.

[0050] When the fluid pressure at the output end 102 rises abnormally and exceeds the preload of the first spring 35, indicating that the output fluid pressure is too high, the fluid pressure pushes the plug body 327 of the second plunger 325 to press against the second retaining ring 316 to form an end-face seal. The reverse swing of the swinging member 32 drives the plug body 327 of the first plunger 324 to press against the first retaining ring 315, completely blocking the communication between the control chamber 104 and the diversion chamber 301. The continuously accumulated fluid pressure in the control chamber 104 pushes the diaphragm 12 downward, ultimately driving the valve disc 15 to form a forced lock with the valve port 103, effectively preventing the abnormal discharge of high-pressure fluid.

[0051] It can be seen that the present invention can achieve dynamic balance and overload protection of the system working pressure through the pilot valve device 3, and is suitable for fluid pressure control under high pressure difference and large flow conditions.

[0052] As attached Figure 4 As shown, the internal structure of the gate valve 2 can be consistent with the gate valve 2 structure in the prior art, including a valve plate 21 and a valve stem 22. The valve stem 22 drives the valve plate 21 to move to realize the fluid on-off control of the gate valve 2. Figures 9 to 12The gate release device 4 includes a split nut 41, a third spring 42, a fourth spring 43, and a rotary disk 44. Two split nuts 41 are provided outside the valve body of the gate valve 2. Both split nuts 41 are slidable relative to the valve body of the gate valve 2. The sliding structure can be such that the valve body of the gate valve 2 is fixed with connection seats 23 on both sides of the valve stem 22, and a guide rod 24 is fixed between the two corresponding connection seats 23. In this way, two parallel guide rods 24 are provided on the valve body of the gate valve 2. Guide holes 411 are provided on both sides of the split nuts 41. The guide holes 411 fit snugly on the outside of the guide rods 24 to form a sliding fit, thereby forming a structure that restricts the split nuts 41 from sliding along the guide rods 24. Both split nuts 41 are provided with a semicircular threaded groove 412 on the side facing the valve stem 22 of the gate valve 2, i.e., the two split nuts 41 are mirror-imaged. A third spring 42 is connected between the two split nuts 41 and the valve body of the gate valve 2. The third spring 42 is sleeved outside the guide rod 24, and the two ends of the third spring 42 are respectively against the connecting rod 14 and the split nut 41, so that the elastic force of the third spring 42 pushes the thread grooves 412 of the two split nuts 41 to the middle of the gate valve 2, and the two thread grooves 412 are spliced ​​to form a complete threaded hole.

[0053] After extending out of the valve body, the valve stem 22 is screwed into the complete threaded hole formed by the two-part nut 41 through threaded engagement. When the operator rotates the valve stem 22, the threaded pair converts the rotational motion into a linear displacement of the valve plate 21, enabling precise adjustment of the opening of the valve plate 21. A fourth spring 43 is connected between the valve plate 21 of the gate valve 2 and the inner wall of the valve body of the gate valve 2. The elastic force of the fourth spring 43 forms a force that pushes the valve plate 21 to close the gate valve 2, so that the preload force of the fourth spring 43 continuously acts on the valve plate 21, giving it a stable closing tendency, and the preload force of the third spring 42 is greater than the preload force of the fourth spring 43. When the system needs to be cut off, the two-part nut 41 separates, causing the threaded hole to disintegrate, and the valve stem 22 is immediately released from the threaded constraint. Driven by the elastic restoring force of the fourth spring 43, the valve plate 21 quickly resets along the axis of the valve stem 22, achieving automatic closing of the gate valve 2.

[0054] As attached Figure 11As shown, the turntable 44 is constrained to rotate outside the valve body of the gate valve 2. Specifically, the valve body of the gate valve 2 forms a raised sleeve 25 on the outside of the end cap. The inner bore of the turntable 44 is adapted to rotate outside this sleeve 25. A retaining spring is embedded in the end of the sleeve 25. This retaining spring, together with the sidewall of the valve body of the gate valve 2, forms an axial limiter for the turntable 44, ensuring smooth rotation within the confined space. Furthermore, a connecting hole is provided through the center of the sleeve 25, into which an oil seal assembly is installed. The valve stem 22 of the gate valve 2 extends through the center hole of the oil seal to the outside of the turntable 44, ensuring the sealing of the valve stem 22 while maintaining its rotational freedom. The turntable 44 has two mirror-image guide grooves 441 on the side facing the outside of the gate valve 2. The path of the guide grooves 441 is an arc eccentric to the turntable 44. A guide pin 413 is provided on the side of the split nut 41 facing the gate valve 2. The guide pins 413 of the two split nuts 41 respectively fit into the two guide grooves 441, forming a sliding fit. When the turntable 44 is driven to rotate, the guide slot 441 rotates accordingly and pushes the guide pin 413 through its side wall to generate radial displacement, forcing the two split nuts 41 to achieve synchronous separation or splicing action.

[0055] Continue to refer to the attached Figure 10 The outer periphery of the turntable 44 is fixed to the ring gear 442, and the protective cover 36 is fixed to the rack 45, with the rack 45 and the ring gear 442 meshing. When the pilot valve assembly 3 needs to be adjusted, the protective cover 36 is slid to expose the pilot valve body 31 and the adjusting screw 34. During this process, the linear displacement of the protective cover 36 is converted into rotational motion of the turntable 44 through the meshing transmission of the rack 45 and the ring gear 442. Furthermore, a slider 462 is fixed to the outside of the valve body of the gate valve 2, and a slide rail 461 is fixed below the rack 45. The slide rail 461 is adapted to slide on the slider 462, thereby improving the smoothness of the sliding process of the protective cover 36. When the turntable 44 rotates, the guide groove 441 on its surface pushes the guide pin 413 to produce radial displacement, forcing the two split nuts 41 on both sides to simultaneously separate along the guide rod 24. After the split nuts 41 separate, the threaded constraint of the valve stem 22 is released, and the gate disc quickly returns along the axis of the valve stem 22 under the elastic restoring force of the fourth spring 43, achieving automatic closing of the gate valve 2. That is, the gate valve 2 can be automatically closed before the pilot valve device 3 is adjusted, which can block the upstream fluid from continuously entering the guide cavity 301, thereby avoiding the dynamic impact of the high-pressure medium on the internal components of the pilot valve body 31 during the adjustment process, resulting in adjustment failure.

[0056] In addition, the pilot valve body 31 can be fixed to the outside of the pressure reducing valve 1 by means of threading bolts, and the connecting plate 37 can be fixed to the end of the pilot valve body 31 facing away from the gate valve 2. When the protective cover 36 slides along the slider to cover the pilot valve body 31, the port of the protective cover 36 can be fitted on the connecting plate 37, and the connecting plate 37 and the protective cover 36 are connected and fixed by a buckle structure, so that the protective cover 36 remains fixed relative to the pressure reducing valve 1 and the gate valve 2, thereby allowing the two-part nut 41 to remain fitted and fixed.

[0057] In summary, the pilot valve device 3 of the present application serves as the pressure regulating center. The swing member 32 swings around the rotation shaft 321 under the driving of fluid pressure, and synchronously drives the first plunger 324 and the second plunger 325 to move axially in opposite directions through the double-sided connecting rod 323. When the high-pressure fluid pushes the first plunger 324 to move into the flow guide cavity 301 to open the high-pressure port 313, the second plunger 325 is synchronously driven to move out of the flow guide cavity 301 to open the low-pressure port 314 to form a pressure relief channel. When the output pressure abnormally rises, the second plunger 325 is reversely driven by the fluid to compress the sealing surface, and the high-pressure port 313 is forcibly closed through the linkage of the swing member 32. The diaphragm 12 of the pressure relief valve 1 drives the valve flap 15 to close the valve port 103, thereby achieving overpressure cut-off and dynamic pressure balance. The safety locking function of the off-gate device 4 of the present application is realized by the sliding protective cover 36 through pure mechanical linkage. The fixed rack 45 drives the peripheral gear ring 442 of the rotating disc 44 to rotate. The eccentric arc guide groove 441 on the surface of the rotating disc 44 pushes the guide pin 413 on the split nut 41 to move radially, forcing the split nut 41 on both sides to overcome the elastic force of the third spring 42 and synchronously separate along the guide rod 24, resulting in the release of the threaded constraint of the valve stem 22. The valve plate 21 of the gate valve 2 is quickly reset to close under the action of the fourth spring 43, synchronously blocking the upstream fluid from entering the flow guide cavity 301 of the pilot valve device 3, thereby eliminating the risk of high-pressure impact and establishing a zero-pressure calibration environment. As can be seen, the integrated fluid control system provided by the present application realizes precise pressure control and intrinsically safe operation under high-pressure conditions through the innovative collaborative mechanism of the pilot valve device 3 and the off-gate device 4.

[0058] The above is only a specific embodiment of the present application, but the design concept of the present application is not limited thereto. Any non-essential modification of the present application using this concept shall be deemed to infringe the protection scope of the present application.

Claims

1. A fluid control system integrating a gate valve and a pressure reducing valve, characterized in that The control system includes a gate valve, a pressure reducing valve and a pilot valve device, wherein the gate valve is connected to the output port of the pressure reducing valve, the pilot valve device is connected to the pressure reducing valve, and the pilot valve device includes: A pilot valve body, wherein a flow guide cavity is formed inside the pilot valve body, and a high-pressure port and a low-pressure port are provided on the pilot valve body, wherein the high-pressure port is connected to the control cavity in the pressure reducing valve, and the low-pressure port is connected to the output end of the pressure reducing valve, and a first retaining ring is provided on the inner annular surface of the high-pressure port, and a second retaining ring is provided on the inner annular surface of the low-pressure port; a swinging member, the swinging member being restricted from swinging in the guide cavity, an adjusting groove being provided in the middle of the swinging member, connecting rods being pivotally connected on both sides of the swinging member relative to the swing axis, the two connecting rods being pivotally connected to a first plunger and a second plunger respectively, the plug body of the first plunger being located in the high-pressure port, and the first plunger being located on a side of the first baffle ring facing the inside of the pilot valve body, the plug body of the second plunger being located in the low-pressure port, and the second plunger being located on a side of the second baffle ring facing the outside of the pilot valve body; a transmission member, the transmission member being arranged in the guide cavity and being swingable, a rotating pin being fixed on one side of the transmission member, the rotating pin passing through the outside of the pilot valve body and fixing a push rod, one end of the transmission member being connected to a rotating wheel, the other end of the transmission member being connected to one end of a first spring, the other end of the first spring being connected to the pilot valve body, so that the elastic preload force of the first spring pulls the rotating wheel to swing upward with the rotating pin as the axis until it tops the adjusting groove; an adjusting screw, the adjusting screw being spirally connected to the pilot valve body and abutting against a side surface of the upper end of the push rod to block the elastic force of the first spring pulling the transmission member to swing; When the high-pressure fluid in the control chamber of the pressure reducing valve overcomes the elastic force of the first spring and enters the guide chamber through the high-pressure port, the high-pressure fluid pushes the first plunger away from the first baffle ring and displaces toward the inside of the guide chamber, causing the swinging member to swing and driving the second plunger to leave the second baffle ring and displace toward the outside of the guide chamber, thereby opening the low-pressure port. When the high-pressure fluid in the output end of the pressure reducing valve overcomes the elastic force of the first spring and enters the pilot valve body through the low-pressure port, the high-pressure fluid pushes the second plunger to press against the second baffle ring, causing the swinging member to swing and driving the first plunger to press against the first baffle ring to seal the high-pressure port.

2. The control system according to claim 1, wherein: The pilot valve body includes a shell and a cover. The internal space when the shell and the cover are closed forms the guide cavity. The high-pressure port and the low-pressure port are both arranged on the cover. The swing member and the transmission member are both arranged in the shell. The adjusting screw is connected to the outside of the shell.

3. The control system according to claim 2, wherein: The cover body is screwed to fix a guide ring in the through holes corresponding to the high-pressure port and the low-pressure port, and a guide hole is formed in the center of the guide ring. The first plunger and the second plunger both include a guide column and the plug body. The guide column and the connecting rod are pivotally connected, and the guide columns are respectively adapted to pass through the guide holes of the guide ring so that the plug body is located in the high-pressure port or the low-pressure port.

4. The control system according to any one of claims 1 to 3, characterized in that: The pilot valve body is spirally connected to a first pipe member and a second pipe member. The high-pressure port is arranged in the first pipe member, and the low-pressure port is arranged in the second pipe member.

5. The control system according to claim 1, wherein: The pilot valve device further includes a protective cover adapted to be mounted outside the pilot valve body and covering the push rod and the adjusting screw.

6. The control system according to claim 1, wherein: The control system also includes a gate-off device, which is arranged on the gate valve. The gate-off device includes a split nut and a third spring and a fourth spring. Both sides of the valve body of the gate valve are connected to slidable split nuts. The two split nuts are provided with a semicircular threaded groove on the side of the valve stem facing the gate valve. The two split nuts are connected to the valve body of the gate valve with a third spring. The elastic force of the third spring pushes the thread grooves of the two split nuts to be spliced ​​toward the middle of the gate valve. After the thread grooves of the two split nuts are spliced, a complete threaded hole is formed. After the valve stem of the gate valve passes through the valve body of the gate valve, it is adapted to spirally pass through the two thread grooves to form a threaded hole. The fourth spring is connected between the valve plate of the gate valve and the inner wall of the valve body of the gate valve. The elastic force of the fourth spring pushes the valve plate to close the gate valve.

7. The control system according to claim 6, wherein: The gate release device also includes a turntable, which is restricted from rotating outside the valve body of the gate valve, and the valve stem passes through the center of the turntable. Two guide grooves are mirror-imaged on the side of the turntable facing the outside of the gate valve, and the path of the guide groove is an arc that is eccentric relative to the turntable; a guide pin is provided on the side of the split nut facing the gate valve, and the guide pins of the two split nuts are respectively embedded in the two guide grooves.

8. The control system according to claim 7, wherein: The pilot valve device also includes a protective cover, which is adapted to be mounted outside the pilot valve body and covers the push rod and the adjusting screw; a gear ring is fixed to the periphery of the turntable, and the protective cover fixes a rack, the rack and the gear ring are engaged, and when the protective cover is slid to open the pilot valve body, the rack is driven to move so that the gear ring rotates accordingly, driving the turntable to rotate, so that the two guide grooves rotate and push the guide pin to move so that the two split nuts are separated.

9. The control system according to claim 8, wherein: A slider is fixed on the valve body of the gate valve, and a slide rail is fixed under the rack. The slide rail is adapted to be embedded in the slider and slide.

10. The control system according to any one of claims 6 to 9, characterized in that: The valve body of the gate valve is fixed with connecting seats on both sides of the valve stem, and a guide rod is fixed between the two corresponding connecting seats. Penetrating guide holes are provided on both sides of the split nut, and the guide holes are adapted to be fitted outside the guide rod. The third spring is sleeved outside the guide rod, and the two ends of the third spring respectively abut against the connecting seat and the split nut.

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