A self-commutated pump drive device for supplying a brazing flux for liquid cooling plate processing

Abstract

This invention relates to a self-reversing pump-driven device for stable flow supply of brazing flux in liquid-cooled plate processing, belonging to the technical field of brazing flux pumping equipment. It includes a valve housing that, together with a variable-capacity diaphragm and a partition plate assembly, defines a dual-path medium-directing valve chamber and a dual-path gas-directing valve chamber that are separated from each other. A diverter input pipe and a combiner output pipe, communicating with the medium-directing valve chamber, are respectively connected to both ends of the valve housing. A linked gas distribution valve assembly is provided on the valve housing, penetrating the partition plate assembly and selectively communicating with the gas-directing valve chamber. Two variable-capacity diaphragms are aligned and arranged within the valve housing cavity in a manner that separates the medium-directing valve chamber and the gas-directing valve chamber. The two variable-capacity diaphragms are linked together by a synchronous horizontal shaft that slides through the partition plate assembly. The linked gas distribution valve assembly is connected to the synchronous horizontal shaft, which undergoes continuous reciprocating lateral movement, via a transmission component penetrating the valve housing. This application can achieve self-reversing function, eliminates the need for a complex external control system, and synchronously achieves stable flow supply during pumping.

Description

Technical Field

[0001] This invention relates to the field of brazing flux pumping equipment, and in particular to a self-reversing pump drive device for stable flow supply of brazing flux for liquid-cooled plate processing. Background Technology

[0002] In the pre-brazing treatment process, where brazing flux is sprayed onto a liquid-cooled plate, a diaphragm pump is typically used to transfer the flux. As an important type of industrial pump, the diaphragm pump possesses a unique isolation function, effectively preventing leakage or contamination of the transported medium, while also protecting other pump components from corrosive or other hazardous media. In practical applications, the diaphragm pump generates periodic volume changes through the reciprocating motion of its flexible diaphragm, thereby ensuring a stable delivery of the brazing flux and guaranteeing the safety and reliability of the entire process. This pump-driven diaphragm pump design not only precisely controls the flux flow rate but also maintains excellent performance under various complex operating conditions, making it an indispensable key piece of equipment in modern industrial production. The diaphragm pump uses a drive system (air, electricity, liquid, etc.) to continuously reciprocate the diaphragm within its chamber, thus cyclically drawing the medium in from the inlet and discharging it from the outlet. Ensuring the smoothness of the entire flux delivery process is paramount. A stable delivery system not only ensures the quality and performance of the brazing flux remain unaffected but also effectively improves work efficiency and reduces unnecessary losses and malfunctions. At the same time, it is worth noting that this process does not require extremely high pressure standards, as excessive pressure may damage equipment and materials, and even affect the final welding result. Therefore, conventional air, electric, and hydraulic drive systems can all meet the pumping requirements of the brazing flux.

[0003] Currently, hydraulically driven diaphragm pumps, a research hotspot in recent years, utilize a hydraulic direct-drive system to replace the traditional reducer and crank-connecting rod mechanism, significantly simplifying the mechanical transmission structure and reducing manufacturing, operating, and maintenance costs. Existing hydraulically driven diaphragm pumps operate by an electric motor driving a hydraulic pump to generate pressurized oil. A directional valve controls the diaphragm pump's hydraulic cylinder to achieve directional control, thus enabling the diaphragm chamber to suck in and discharge materials. However, to reduce fluctuations in the flow parameters of the pumped medium, a dual-chamber or multi-chamber structure is typically considered to improve the smoothness of medium delivery. However, existing hydraulically driven dual-chamber diaphragm pumps often rely on complex electronic control systems or multiple independent hydraulic directional valve assemblies to control the alternating movements of different diaphragms during the directional switching process. Furthermore, multiple diaphragm level detection and feedback modules are required for station monitoring. This makes the control system, which uses solenoid valves to control the hydraulic cylinder directional switching, more complex, reduces the reliability of the directional switching control system, and increases system complexity and cost. It can also cause instantaneous fluctuations in media delivery pressure and flow rate due to directional switching delays, affecting the stability of brazing flux supply. Additionally, it may lead to incomplete brazing or filler metal accumulation in liquid-cooled plate brazing, directly impacting the brazing quality in liquid-cooled plate processing scenarios. Moreover, the traditional diaphragm pump's gas or liquid distribution structure has a slow linkage response speed with the diaphragm, exhibiting feedback lag and making it difficult to achieve highly coordinated synchronous directional switching movements, further exacerbating the pulsation phenomenon of the output medium. Meanwhile, for mixed media like brazing flux, which have a certain viscosity and are prone to sedimentation, the dual-chamber structure alone is sometimes insufficient to completely eliminate flow fluctuations, requiring an additional flow stabilizing device for secondary adjustment. However, the adjustment response of the external flow stabilizing device often lags behind the flow changes of the pump itself, resulting in limited flow stabilization effect. Finally, when the diaphragm is damaged, hydraulic oil may mix into the brazing flux, causing medium contamination, affecting the brazing quality of the liquid cooling plate, and increasing the difficulty of subsequent pump repair. Summary of the Invention

[0004] The purpose of this invention is to provide a flux pump drive device for liquid-cooled plate processing that can achieve self-reversing function, requires no complex external control system, and can synchronously achieve stable flow supply during pumping. This addresses the problems of existing hydraulically driven dual-chamber diaphragm pumps, which rely on complex electronic control systems or independent hydraulic directional valve groups to control the alternating action of the diaphragm during flux delivery, and require additional diaphragm level detection and feedback modules for point monitoring, resulting in increased control system complexity and cost. Furthermore, traditional gas or liquid distribution structures have slow linkage response with the diaphragm, exacerbating the pulsation of the output medium, and conventional external flow stabilization devices suffer from lag in adjustment response. In addition, diaphragm damage can cause hydraulic oil contamination of the flux, affecting the brazing quality of the liquid-cooled plate and increasing the difficulty of subsequent pump repair.

[0005] The technical solution adopted in this invention is as follows: a self-reversing pump drive device for stable flow supply of brazing flux in liquid-cooled plate processing, comprising a valve housing, with a diverting input pipe and a converging output pipe respectively connected to both ends of the valve housing, capable of communicating with the medium guiding valve chamber; a linkage gas distribution valve group is also provided on the valve housing, penetrating a partition plate assembly and selectively communicating with two parallel gas guiding valve chambers; and the linkage gas distribution valve group can switch the input path and output path of high-pressure gas flow into and out of the gas guiding valve chamber in conjunction with the working state of the variable-capacity diaphragm, wherein the central gas guiding chamber shell of the valve housing is divided into... The two symmetrically distributed local cavities separated by the vertical thick plate of the partition group are gas guiding valve cavities. The extended cavity shell of the valve shell and the medium guiding pipe shell together define the medium guiding valve cavity. The two variable-capacity diaphragms are arranged in alignment at both ends of the central gas guiding cavity shell in a manner that separates the medium guiding valve cavity from the gas guiding valve cavity. The two variable-capacity diaphragms are linked together by a synchronous horizontal shaft, and the synchronous horizontal shaft is slidably inserted into the through hole of the vertical thick plate. The linked gas distribution valve group is connected to the synchronous horizontal shaft, which undergoes continuous reciprocating lateral movement, through a transmission component that passes through the valve shell. Its advantages lie in the fact that by synchronously moving the horizontal axis back and forth, the linkage gas distribution valve group can be driven to complete the gas guide path switching in sync. No additional electronic control reversing unit and diaphragm level detection feedback module are required. Gas distribution reversal can be achieved by the movement of the diaphragm itself, which greatly simplifies the overall structure and control system and reduces the equipment manufacturing cost. At the same time, the movement of the diaphragm and the gas distribution reversal are directly linked, with fast response speed, eliminating the flow and pressure fluctuations caused by reversal delay, and effectively improving the stability of the brazing flux supply. Furthermore, the use of high-pressure airflow as the driving force means that even if the diaphragm is damaged, only gas will mix into the brazing flux, and there will be no problem of hydraulic oil contamination of the medium. This ensures the purity of the brazing flux, reduces the difficulty of later repair and maintenance of the pump body, and is more suitable for the working conditions of brazing flux delivery in liquid cooling plate processing.

[0006] According to a preferred embodiment, symmetrically arranged expansion chamber shells are provided on both sides of the centrally located gas guide chamber shell, and a medium guide pipe shell is connected to the side of the expansion chamber shell away from the centrally located gas guide chamber shell. The variable-capacity diaphragm is sandwiched between the centrally located gas guide chamber shell and the expansion chamber shell. The partition plate assembly is centrally installed within the centrally located gas guide chamber shell, dividing it into two symmetrically arranged gas guide valve chambers. Its advantage lies in that this symmetrical dual-chamber arrangement allows the movement of the two variable-capacity diaphragms to remain synchronized, resulting in a smoother connection between the material suction and discharge processes. This helps reduce pulsation during the flux delivery process. Furthermore, the separate arrangement of the gas drive chamber and the medium delivery chamber results in a neat structure, facilitating the integrated installation of the linkage gas distribution valve assembly and simplifying subsequent maintenance and repair of each chamber.

[0007] According to a preferred embodiment, the linkage gas distribution valve assembly includes a dual-chamber gas distribution valve that is embedded in the centrally located gas guide chamber housing through the partition plate assembly and can switch the input and output paths of the high-pressure gas flow into and out of the dual-path gas guide valve chambers, and a front-mounted linkage valve that is connected to the dual-chamber gas distribution valve via a gas guide pipeline and can drive the dual-chamber gas distribution valve to switch the gas guide path. Its advantage lies in that the dual-chamber gas distribution valve is directly integrated into the centrally located gas guide chamber housing, enabling simultaneous switching of the gas guide paths in the two gas guide valve chambers. Combined with the driving action of the front-mounted linkage valve, this reduces the need for additional piping and ensures a fast response time for the reversing action, maintaining high synchronization between the gas guide path switching and the reciprocating lateral movement of the synchronous horizontal axis, further reducing flow fluctuations caused by reversing delays.

[0008] According to a preferred embodiment, the first embedded valve body of the dual-chamber gas distribution valve is embedded in the centrally located air guide chamber shell; a first valve core is slidably inserted into the valve chamber of the first embedded valve body, and piston plates that cooperate with the valve chamber of the first embedded valve body to define two symmetrically arranged variable-capacity adjusting gas chambers are connected to both axial ends of the first valve core; adjusting connecting pipes communicating with the variable-capacity adjusting gas chambers are also inserted into both axial ends of the first embedded valve body.

[0009] According to a preferred embodiment, the second pilot valve body of the pre-mounted linkage valve is detachably mounted on the outward mounting plate of the central air guide chamber shell, and a second linkage valve core is axially slidably inserted into the second pilot valve body; a shifting sleeve that slides through the second pilot valve body is coaxially connected to one end of the second linkage valve core, and a linkage push-pull rod is also slidably inserted into the shifting sleeve.

[0010] According to a preferred embodiment, the rolling drive wheel of the transmission assembly is mounted on the transmission shaft, and the transmission shaft is rotatably inserted into the centrally located air guide chamber housing, such that the rolling drive wheel is in rolling contact with the synchronous horizontal shaft. Its advantages are that the line-contact rolling connection transmission method can smoothly convert the reciprocating lateral movement of the synchronous horizontal shaft into the rotational motion of the transmission shaft, achieving power transmission without the need for complex meshing transmission structures. It has low processing and assembly difficulty, low wear during operation, effectively reduces the transmission resistance of reversing actions, ensures the switching response speed of the linked air distribution valve group, and has lower maintenance and replacement costs after long-term operation.

[0011] According to a preferred embodiment, the transmission shaft extends to one end of the outer side of the centrally located air guide chamber shell and is coaxially connected to a rotating screw, and a transmission nut is fitted on the rotating screw; the guide rail of the transmission assembly is mounted on the outward mounting plate, and a guide slider fitted on the transmission nut is slidably mounted in the groove of the guide rail; the guide slider is also connected to the end of the linkage push-pull rod away from the second pilot valve body.

[0012] According to a preferred embodiment, a linkage tube with an adaptive flow stabilizing component is inserted into the shell wall of the medium guide tube housing. This linkage tube is also connected to a flow stabilizing regulating tube inserted into the outlet branch of the manifold output pipe via an external equivalent pipeline. Its advantage lies in that the pressure change within the medium guide valve cavity drives the linkage tube to move, simultaneously adjusting the flow stabilizing regulating tube's cross-section of the manifold output pipe. This allows for direct triggering of flow stabilization based on medium pressure changes when the pump output flow rate fluctuates instantaneously, eliminating the need for additional power input and detection control units. The adjustment response is synchronized with flow fluctuations, effectively solving the problem of delayed adjustment response from external flow stabilizing devices and further ensuring the stability of the brazing flux output flow rate.

[0013] According to a preferred embodiment, the first shell of the linkage tube is inserted into the shell wall of the medium guide tube shell, and a first piston body capable of variable-volume separation of its cavity is provided inside the first shell; the closed end of the linkage tube is also slidably fitted with a limiting slide rod capable of limiting the translational distance of the first piston body, and a communicating tube connected to the axial end face of the first shell is also fitted on the limiting slide rod.

[0014] According to a preferred embodiment, the flow regulating tube includes a second shell inserted into the side wall of the outflow branch pipe, a second piston body disposed in the second shell, and a flow limiting column connected to the second piston body and capable of changing the flow guiding cross-section size of the outflow branch pipe by partially moving into the outflow branch pipe; the end of the second piston body away from the flow limiting column is also connected to an elastic limiting spring that limits its initial position in the second shell.

[0015] The beneficial effects of this invention are: This invention achieves synchronized gas distribution path switching by driving the reciprocating lateral movement of the synchronous horizontal axis to drive the linkage gas distribution valve group. It eliminates the need for additional electronic control reversing units and diaphragm level detection feedback modules, relying solely on the movement of the variable-capacity diaphragm to realize automatic gas distribution reversal. This significantly simplifies the overall pump structure and control system, effectively reducing equipment manufacturing costs. Secondly, the direct linkage between the movement of the variable-capacity diaphragm and gas distribution reversal results in a fast response, greatly eliminating instantaneous fluctuations in flux flow and pressure caused by reversal delays. This effectively improves the stability of flux supply, avoiding problems such as insufficient local brazing or filler metal accumulation in liquid-cooled plate brazing, thus ensuring the brazing quality of the liquid-cooled plate. Furthermore, this invention employs… Using high-pressure airflow as the driving force, even if the diaphragm is damaged, only gas will mix into the brazing flux, preventing hydraulic oil from contaminating the medium. This ensures the purity of the brazing flux and reduces the difficulty of later pump repair and maintenance, making it more suitable for the working conditions of brazing flux delivery in liquid-cooled plate processing. Finally, this invention integrates an adaptive flow stabilization component that is linked to the pressure of the medium delivery chamber. It can synchronously trigger the adjustment of the flow cross section of the manifold output pipe based on changes in medium pressure. The adjustment response is synchronized with the flow fluctuation, effectively solving the problem of lag in the adjustment response of external flow stabilization devices. This further ensures the stability and reliability of the brazing flux output flow rate, meeting the requirements of stable brazing flux supply in liquid-cooled plate processing. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of a preferred self-reversing pump drive device for stable flow supply of brazing flux in liquid-cooled plate processing proposed in this invention. Figure 2 This is a cross-sectional schematic diagram at AA of a preferred self-reversing pump drive device for stabilizing the flow of solder flux for liquid-cooled plate processing proposed in this invention. Figure 3 This is a partial cross-sectional schematic diagram at BB of a preferred self-reversing pump drive device for stabilizing the flow of solder flux for liquid-cooled plate processing proposed in this invention. Figure 4 This is a side plan view of the centrally located air guide chamber shell of a preferred self-reversing pump drive device for stable flow supply of brazing flux in liquid-cooled plate processing proposed in this invention. Figure 5 This is a partial cross-sectional schematic diagram of the dual-chamber gas distribution valve of a preferred self-reversing pump-driven device for stabilizing the flow of brazing flux for liquid-cooled plate processing proposed in this invention under another working condition. Figure 6 This is a cross-sectional schematic diagram of the linkage gas distribution valve group of a preferred self-reversing pump-driven device for stable flow supply of brazing flux in liquid-cooled plate processing proposed in this invention. Figure 7This is a cross-sectional schematic diagram of the linkage gas distribution valve group of a preferred self-reversing pump-driven device for stabilizing the flow of brazing flux for liquid-cooled plate processing proposed in this invention under another working condition.

[0017] List of reference numerals 1: Valve housing; 2: Flow input pipe; 3: Flow output pipe; 4: Adaptive flow stabilization assembly; 5: Linked gas distribution valve assembly; 6: Variable capacity diaphragm; 7: Synchronous horizontal shaft; 8: Divider plate assembly; 9: Transmission assembly; 11: Centrally located air guide chamber shell; 12: Expansion chamber shell; 13: Medium flow guide pipe shell; 14: Self-sealing check valve; 111: Outward mounting plate; 21: Inlet branch pipe; 22: Inlet main pipe; 31: Outlet branch pipe; 32: Flow main pipe; 41: Linked pipe sleeve; 42: External equivalent pipeline; 43 411: Flow regulating tube; 412: First cylinder shell; 413: First piston body; 414: Limiting slide rod; 415: Connecting tube; 416: Third piston body; 431: Second cylinder shell; 432: Second piston body; 433: Flow limiting column; 434: Elastic limiting tension spring; 51: Dual-chamber gas distribution valve; 52: Pre-mounted linkage valve; 53: Gas guide line; 511: First embedded valve body; 512: First valve core; 513: Piston plate; 514: Adjustment connecting pipe head; 521: Second pilot valve body 522: Second linkage valve core; 523: Shifting sleeve; 524: Linkage push-pull rod; 5111: First air inlet; 5112: Second air inlet; 5113: First air outlet; 5114: Second air outlet; 5115: First input port; 5116: Second input port; 5117: First output port; 5118: Second output port; 5121: First air inlet guide groove; 5122: Second air inlet guide groove; 5123: First exhaust guide groove; 5124: Second exhaust guide groove; 5211: Gas inlet; 5212: First gas outlet; 5213: Second gas outlet; 5214: Pressure relief port; 61: Diaphragm body; 62: Reinforcing positioning ring edge; 63: Connecting seat; 71: Rolled groove; 81: Vertical thick plate; 82: Bolt tie rod; 811: Through hole; 812: Sliding sealing ring; 813: Sealing protrusion; 91: Rolled drive wheel; 92: Drive shaft; 93: Rotating screw; 94: Drive nut; 95: Guide slider; 96: Guide rail. Detailed Implementation

[0018] The following is a detailed explanation with reference to the accompanying drawings.

[0019] This application provides a self-reversing pump drive device for stabilizing the flow of brazing flux for liquid-cooled plate processing, which includes a valve housing 1, a diverter input pipe 2, a combiner output pipe 3, an adaptive flow stabilization component 4, a linkage gas distribution valve group 5, a variable capacity diaphragm 6, a synchronous horizontal shaft 7, a partition plate group 8, and a transmission component 9.

[0020] according to Figures 1-7In one specific embodiment, the valve housing 1, together with the variable-capacity diaphragm 6 and the partition plate assembly 8, defines a dual-path medium-direction valve chamber and a dual-path gas-direction valve chamber that are separated from each other. This allows the high-pressure gas flow through the dual-path gas-direction valve chamber to change the chamber volume and pressure of the dual-path medium-direction valve chamber by forcing the variable-capacity diaphragm 6 to deform, thereby drawing the medium into and out of the dual-path medium-direction valve chamber and forming a directional flow of the medium. A diversion input pipe 2 and a confluence output pipe 3, which communicate with the two medium-direction valve chambers, are respectively connected to both ends of the valve housing 1. An adaptive flow stabilizing component 4 is also connected between the valve housing 1 and the confluence output pipe 3 to mitigate excess fluid pressure when the medium is pumped out of the medium-direction valve chamber. The adaptive flow stabilizing component 4 absorbs or releases part of the medium by changing its own volume communicating with the medium-direction valve chamber, thus helping to stabilize the pressure within the medium-direction valve chamber. A linkage gas distribution valve assembly 5, which penetrates the partition plate assembly 8 and selectively communicates with the dual-path gas-direction valve chamber, is also provided on the valve housing 1. The linkage valve assembly 5 can switch the input and output paths of high-pressure gas flow into and out of the dual-channel gas guide valve chamber in conjunction with the working state of the variable-capacity diaphragm 6. The two variable-capacity diaphragms 6 are aligned and arranged within the valve housing 1 in a manner that separates the medium guide valve chamber from the gas guide valve chamber. The two variable-capacity diaphragms 6 are linked together by a synchronous horizontal shaft 7 that slides through and is installed within the valve housing 1, connected to the front linkage valve 52 of the linkage valve assembly 5 via a transmission assembly 9. This synchronous horizontal shaft 7 continuously reciprocates according to the deformation of the variable-capacity diaphragm 6. The end of the transmission assembly 9 furthest from the front linkage valve 52 is rotatably inserted into the valve housing 1 in a manner that it rolls into contact with the portion of the synchronous horizontal shaft 7 within the partition plate assembly 8. This allows the continuously reciprocating synchronous horizontal shaft 7 to interlock the operating conditions of the front linkage valve 52, thereby periodically switching the gas guide path of the dual-chamber gas distribution valve 51. This application eliminates the need for complex electronic control systems and additional membrane level detection feedback modules. It relies solely on the synchronous horizontal axis 7, linked to the variable-capacity diaphragm 6, to drive the gas distribution path switching. This achieves self-reversing control of alternating action of the two diaphragms, simplifying the overall structural complexity of the device, reducing costs, and avoiding fluctuations in medium delivery pressure and flow rate caused by electronic control reversing delays, thus ensuring the stability of the brazing flux supply. Since the linked gas distribution valve group 5 operates synchronously with the variable-capacity diaphragm 6, there is no feedback lag problem, enabling highly coordinated synchronous reversing and effectively mitigating the pulsation phenomenon in brazing flux delivery. The adaptive flow stabilization component 4 can synchronously adjust the effective flow guide cross-section of the manifold output pipe according to the pressure changes in the medium guide valve chamber, eliminating the adjustment response lag problem of external flow stabilization devices. This further improves the stability of brazing flux output and ensures the brazing quality of the liquid-cooled plate. Furthermore, this application uses pollution-free high-pressure gas to drive the variable-capacity diaphragm. Even if the variable-capacity diaphragm is damaged, only clean high-pressure gas mixes into the brazing flux, without contaminating the flux or significantly increasing the difficulty of subsequent pump repair.

[0021] This application uses compressed air as its power source. The exhaust process involves expansion and heat absorption, causing the diaphragm pump's temperature to decrease as its operating state changes. The entire process does not emit harmful gases. When used for conveying brazing flux containing suspended flux particles, a pneumatic diaphragm pump capable of conveying fluids with viscosities up to 150,000 centipoise and allowing solid particles with a particle size of 60 mm or less can fully meet the conveying requirements. Furthermore, the gas-driven method only requires connection to an external high-pressure air source that can continuously provide high-pressure airflow via an air pipe. Remote deployment of the air source ensures no motor or spark generation, meeting the safety requirements of flammable and explosive environments in welding workshops. The alternating pumping mechanism of the dual-path medium diversion valve chamber in this application can dynamically absorb pressure peaks in the pipeline system and compensate for troughs generated during flow fluctuations, thereby ensuring that pressure fluctuations throughout the pipeline system can be strictly controlled within a small threshold range.

[0022] like Figure 1As shown, symmetrically arranged on both sides of the centrally located gas guide chamber shell 11 of the valve shell 1 are extended chamber shells 12 connected to the side openings of the shell. More preferably, a medium guide tube shell 13, communicating with the cavity of the extended chamber shell 12, is integrally connected to the side of the extended chamber shell 12 away from the centrally located gas guide chamber shell 11. Preferably, a variable-capacity diaphragm 6 is sandwiched between the centrally located gas guide chamber shell 11 and the extended chamber shell 12 to isolate and seal the chamber docking openings of both, thus separating the gas guide valve cavity defined by the centrally located gas guide chamber shell 11 from the medium guide valve cavity jointly defined by the extended chamber shell 12 and the medium guide tube shell 13. Preferably, a partition plate assembly 8 is centrally installed within the centrally located gas guide chamber shell 11 to separate two symmetrically arranged gas guide valve cavities. Preferably, at the medium inlet and medium outlet, which are connected to the medium guide tube shell 13 and the diversion input pipe 2 and the junction output pipe 3, a self-closing check valve 14 is respectively provided, allowing the medium to be input in one direction under negative pressure and output in one direction under pressurized condition. Preferably, the self-closing check valve 14 can be the diaphragm pump ball valve disclosed in patent document CN121676368A. Specifically, the self-closing check valve 14 near the diversion input pipe 2 and the self-closing check valve 14 near the manifold output pipe 3 can alternately conduct when the variable-capacity diaphragm 6 changes the internal pressure of the medium guiding valve cavity by causing diaphragm deformation. That is, when the volume of the medium guiding valve cavity decreases and the internal pressure increases, the self-closing check valve 14 near the diversion input pipe 2 closes and the self-closing check valve 14 near the manifold output pipe 3 conducts, so that the medium in the medium guiding valve cavity is discharged. When the volume of the medium guiding valve cavity increases and a negative pressure is generated in the cavity, the self-closing check valve 14 near the diversion input pipe 2 conducts and the self-closing check valve 14 near the manifold output pipe 3 closes, and the medium enters the medium guiding valve cavity from the diversion input pipe 2, balancing the negative pressure of the medium guiding valve cavity when the volume increases. The one-way flow characteristic of the self-closing check valve 14 effectively avoids backflow that may occur during the transport of the medium, ensuring that the brazing flux can flow stably in the predetermined direction, and providing a basic guarantee for the precise supply of brazing flux during the liquid cooling plate processing.

[0023] Preferably, an extended mounting plate 111 is integrally formed or welded to the side of the centrally located air guide chamber shell 11. A removable cover can also be configured on the extended mounting plate 111 as needed to protect external components. The extended mounting plate 111 provides a stable mounting base for the pre-operated linkage valve 52 in the linked air distribution valve assembly 5, enabling it to effectively link with the internal structure of the valve shell 1. Specifically, the second pilot valve body 521 of the pre-operated linkage valve 52 is mounted on the extended mounting plate 111 via a detachable connection such as bolts, ensuring convenience during equipment maintenance or component replacement. The positional design of the extended mounting plate 111 exposes the connection area between the pre-operated linkage valve 52 and the transmission assembly 9, facilitating necessary adjustments and observations by operators. Simultaneously, its integrated connection with the centrally located air guide chamber shell 11 ensures the rigidity of the overall structure, reducing component displacement or loosening due to vibration and other factors, thereby maintaining the stability and reliability of the linked air distribution valve assembly 5.

[0024] like Figure 1 As shown, the diversion input pipe 2 includes inlet branch pipes 21 and inlet main pipe 22. Preferably, the two inlet branch pipes 21 are connected to the input ports of the dual-path medium guiding valve chambers defined by two parallel medium guiding pipe shells 13 via flange bolts. More preferably, the input ends of the two inlet branch pipes 21 are connected to an external brazing flux storage device or other medium storage module via the same inlet main pipe 22, thereby directionally conveying the medium under negative pressure. A check valve, filter, and flow monitoring instrument can be installed on the inlet main pipe 22 according to actual needs. The filter can effectively remove impurity particles from the brazing flux, preventing impurities from entering the pump drive device and causing component wear or blockage, ensuring the cleanliness of the medium. The flow monitoring instrument can display the flow rate of the brazing flux entering the device in real time, providing intuitive data support for operators to monitor and adjust the supply.

[0025] like Figure 1 As shown, the manifold output pipe 3 includes an outflow branch pipe 31 and a manifold main pipe 32. Preferably, the outflow branch pipe 31 is connected to the output ports of the dual-path medium guiding valve chambers defined by two parallel medium guiding pipe shells 13 via flange bolts. More preferably, the output ends of the two outflow branch pipes 31 are connected to the brazing flux spraying module via the same manifold main pipe 32, ultimately delivering the brazing flux liquid, after flow stabilization treatment, to the brazing station of the liquid-cooled plate processing. A pressure sensor can also be installed on the manifold main pipe 32 to monitor the pressure of the output brazing flux. When abnormal pressure fluctuations occur, the sensor can promptly feed back to the control system, facilitating corresponding remedial maintenance or adjustment measures to ensure a stable pressure supply of the brazing flux, meeting the stringent requirements of the liquid-cooled plate brazing process for medium pressure.

[0026] Preferably, an adaptive flow stabilizing component 4 is inserted into the shell wall of the medium guide tube shell 13 of the valve shell 1, forming a linkage tube 41. More preferably, the linkage tube 41 is also connected to a flow stabilizing regulating tube 43 inserted into the outlet branch pipe 31 of the manifold output pipe 3 via an external equivalent pipe 42. The adaptive flow stabilizing component 4 provided in this application can replace the traditional combined external flow stabilizing structure composed of a pulse damper and a back pressure valve. It can adjust the flow channel cross-section and the additional volume of the medium guide valve cavity in a timely manner according to the fluctuation of the medium flow pressure, thereby smoothing pressure and flow fluctuations and achieving a more precise and dynamic flow stabilizing effect. The linkage pipe 41, connected to the flow stabilization pipe 43 via the external equivalent pipe 42, combines the feedback regulation of flow and pressure with the cavity compensation of the medium guiding valve chamber, forming a closed-loop dynamic regulation system. Compared with traditional passive flow stabilization devices, it has a faster response speed and higher regulation accuracy, and can more effectively suppress pressure and flow fluctuations during the brazing flux delivery process, ensuring that the parameters of the brazing flux liquid flow delivered to the brazing station are stable within the process requirements, which is beneficial to improving the quality consistency and reliability of liquid-cooled plate brazing. The adaptive flow stabilization component 4 reduces the pressure peak caused by flow fluctuations by dynamically absorbing the excess pressure in the pumping system. This process can not only respond to instantaneous changes in pressure and flow in a timely manner, but also maintain the stability of the system, avoiding the impact of excessive fluctuations on the normal operation of equipment or causing safety hazards, thereby ensuring the smoothness and reliability of pipeline transportation. In addition, the adaptive flow stabilization component 4 has a post-pressure regulation capability, which can effectively cooperate with the final inertial flow generated during the diaphragm pumping process. This cooperative relationship means that during the entire system operation, the adaptive flow stabilization component 4 will precisely adjust and control the pressure according to the specific working conditions. During diaphragm pumping, the flow rate formed at the end of its single-process movement due to inertia can achieve a more stable and expected flow state under the pressure regulation of the adaptive flow stabilization component 4, thereby ensuring the efficiency and stability of the entire system in fluid transmission. The adaptive flow stabilization component 4 enables the medium pressure in the manifold output pipe 3 to remain stable during the gap between the pumping and discharging actions when the single-sided medium guide valve chamber completes the discharge reversal. This effectively matches the delayed decay during medium pumping, compensates for the pressure weakening that occurs when switching from suction to discharge on one side, fills the flow gap between the alternating pumping of the dual-channel medium guide valve chambers, avoids the periodic pressure drop caused by the reversal gap in conventional dual-diaphragm pumping systems, further reduces the range of pressure and flow fluctuations during the entire transportation process, and ensures the continuity and stability of the brazing flux supply. The adaptive flow stabilization component 4 can significantly reduce the pressure fluctuation of the output brazing flux during pumping without adding an external voltage stabilization device. This avoids the problem of increased pipeline pressure loss caused by the addition of a damping structure in traditional devices. While ensuring the flow stabilization effect, it reduces unnecessary energy loss and improves the energy utilization efficiency of the entire pump drive system.

[0027] like Figure 1 As shown, the first shell 411 of the linkage tube 41 is inserted into the shell wall of the medium guide tube 13 in a manner that connects it to the medium guide tube shell 13. More preferably, a first piston body 412 capable of variable-volume partitioning its cavity is provided inside the first shell 411. The first piston body 412 changes the volume of the cavity communicating between the first shell 411 and the medium guide tube shell 13 by axially translating within the first shell 411. Specifically, the first piston body 412 is composed of a cylinder and a frustum-shaped body disposed at the end of the cylinder, such that the first cylindrical shell 411, which has an end through-hole matching the frustum-shaped body, can cooperate with the limiting slide rod 413 to limit the axial translational range of the first piston body 412. When the first cylindrical shell 411 is pre-filled with gas to provide an initial inflation pressure, the frustum-shaped body of the first piston body 412 is embedded in the end through-hole of the first cylindrical shell 411, so that the first piston body 412 absorbs part of the medium only when the flux pumping pressure in the medium guiding valve cavity exceeds a preset rated value, thereby helping to stabilize the pressure in the medium guiding valve cavity. Preferably, the closed end of the linkage tube 41 is also slidably fitted with a limiting slide rod 413 that can limit the translational distance of the first piston body 412 in the linkage tube 41. More preferably, a connecting tube 414 connected to the axial end face of the first cylindrical shell 411 is also fitted on the limiting slide rod 413. Preferably, the insertion front end of the limiting slide rod 413 is connected to the first piston body 412, and the portion of the limiting slide rod 413 that slides through the first sealing end cap of the first cylindrical shell 411 is slidably inserted into the connecting tube 414. Specifically, the connecting tube 414 is coaxially mounted on the first sealing end cap of the first cylindrical shell 411 via a seamless flange sealing connection. Preferably, the connecting tube 414 is mounted on the side wall of the second cylindrical shell 431 such that its end away from the first cylindrical shell 411 is connected to the second cylindrical shell 431. More preferably, the end of the limiting slide rod 413 inside the connecting tube 414 is also connected to a third piston body 415. Preferably, a sealing gasket is provided in the through hole of the first sealing end cap of the first cylindrical shell 411 where the limiting slide rod 413 is inserted. More preferably, the first sealing end cap is also provided with a gas filling port, which facilitates the pre-filling of a certain amount of pressurized gas according to the rated pressure requirement. Preferably, an external equivalent conduit 42 is also inserted into the first sealing end cap of the first cylindrical shell 411. The limiting slide rod 413 is used to limit the translational distance of the first piston body 412 to prevent excessive movement that could lead to inaccurate flow stabilization or component damage. The connecting tube 414 connects the limiting slide rod 413 to the axial end face of the first cylindrical shell 411, serving both as a guide and providing stable support for the movement of the limiting slide rod 413.

[0028] like Figure 1As shown, the flow regulating tube 43 includes a second shell 431 inserted into the side wall of the outflow branch pipe 31, a second piston body 432 disposed in the second shell 431, and a flow-limiting column 433 connected to the second piston body 432 and capable of changing the flow-guiding cross-section of the outflow branch pipe 31 by partially moving into the outflow branch pipe 31. Preferably, the end of the second piston body 432 away from the flow-limiting column 433 is also connected to an elastic limiting spring 434 that limits its initial position in the second shell 431. Specifically, in the initial state, the elastic limiting spring 434 is in a state of force balance and extension under the action of the internal gas pressure of the second shell 431, so that the flow-limiting column 433 is just accommodated in the second shell 431. Therefore, when the internal gas pressure of the second shell 431 increases, the second piston body 432 is translated by overcoming the tension of the elastic limiting spring 434, so that the flow-limiting column 433 is partially moved out of the second shell 431. Preferably, the second piston body 432 has a rectangular cross-section that matches the second cylindrical shell 431 and the flow-limiting column 433. Preferably, the end of the flow-limiting column 433 that can be moved into the outflow branch pipe 31 is curved. Preferably, the end of the elastic limiting spring 434 away from the second piston body 432 is connected to the second sealing end cap of the second cylindrical shell 431. More preferably, the elastic limiting spring 434 can be connected to the second sealing end cap through a connecting plate with a telescopic screw, that is, the elastic limiting spring 434 is mounted on the connecting plate, and the connecting plate is threaded into the second sealing end cap through a telescopic screw integrally connected to it, so that the depth of the connecting plate and the telescopic screw inserted into the second sealing end cap can be changed by rotation. The second sealing end cap is detachably sealed and fastened to the end of the second cylindrical shell 431, which facilitates the maintenance and replacement of the elastic limiting spring 434. Preferably, the end of the external equivalent conduit 42 away from the first shell 411 is connected to the side of the second shell 431, thereby connecting the first shell 411 and the second shell 431 and maintaining air pressure balance in their sealed cavities. Preferably, an inflation and pressurization port is also provided on the second sealing end cap, thereby facilitating pre-inflation and pressurization to define the initial working position of the first piston body 412 and the second piston body 432.

[0029] When the variable-capacity diaphragm 6 deforms towards the medium flow valve cavity under the pressure of the high-pressure airflow, compressing the volume of the medium flow valve cavity, the medium flow pressure in the medium flow valve cavity begins to increase. When the medium flow pressure exceeds the initial back pressure of the first piston body 412, it pushes the first piston body 412 in the first cylinder shell 411 to move away from the medium flow pipe shell 13. The movement of the first piston body 412 causes the limiting slide rod 413 connected to it to slide in the connecting pipe 414, while compressing the gas in the first cylinder shell 411. The compressed gas enters the second cylinder shell 431 through the external equivalent pipe 42, and the limiting slide rod 413 drives the third piston body 415 to move towards the second cylinder shell 431, thereby reducing the cylinder cavity connected to the second cylinder shell 431 by the connecting pipe 414. The pressurized gas entering the second shell 431 and the increased pressure due to the reduced cavity size work together to push the second piston 432 against the tension of the elastic limiting spring 434 towards the outlet branch pipe 31, thereby causing the flow-limiting column 433 to partially enter the outlet branch pipe 31. Since the end of the flow-limiting column 433 is curved, its entry into the outlet branch pipe 31 gradually reduces the minimum flow cross-sectional area of ​​the outlet branch pipe 31, thus suppressing excessively high instantaneous flow and pressure peaks exceeding the rated value caused by the compression of the medium flow-guiding valve cavity. Conversely, at the end of a complete drainage stroke of the medium flow-guiding valve cavity, the pumping pressure of the medium flow in the medium flow-guiding valve cavity decreases, and the elastic limiting spring 434 pulls the second piston 432 and the flow-limiting column 433 back, increasing the flow cross-sectional area, reducing resistance, and increasing the flow rate. Simultaneously, the first piston 412 slides within the first shell 411 in response to pressure changes within the medium flow-guiding valve cavity. The first piston 412 inside the first shell 411 resets towards the medium guide tube shell 13 under the action of the medium pressure (or initial inflation pressure) on its other side. At this time, the gas pressure in the cylinder between the first piston 412 and the first sealing end cap in the first shell 411 decreases. Under the reset pulling force of the elastic limiting spring 434, the gas in the second shell 431 flows back to the first shell 411 through the external equivalent pipeline 42. The second piston 432 drives the flow limiting column 433 to exit from the outlet branch pipe 31. The flow cross-sectional area of ​​the outlet branch pipe 31 is restored, the flow resistance is reduced, and the flow and pressure troughs that may occur due to the increase in the volume of the medium guide valve cavity are avoided. The movement of the first piston 412 can change the volume of the cylinder cavity of the linkage tube 41, thereby compensating for the pressure of the medium in the medium guide tube shell 13. That is, the first piston 412 in the linkage tube 41 moves accordingly, and absorbs or releases part of the medium by changing its own volume, which helps to stabilize the pressure in the medium guide valve cavity and avoids the pressure pulse caused by the periodic action of the variable displacement diaphragm 6 from being transmitted to the subsequent pipeline.This application uses an adaptive flow stabilizing component 4 with such a linkage adjustment mechanism to respond in real time to changes in medium flow pressure, dynamically adjust the flow cross section of the outflow branch pipe 31 and the effective cavity volume of the medium guiding valve chamber, thereby significantly reducing pressure and flow pulsation during medium transportation and achieving a stable supply of brazing flux.

[0030] like Figures 2-7 As shown, the linkage gas distribution valve assembly 5 includes a dual-chamber gas distribution valve 51, which is embedded in the central gas guide chamber shell 11 by means of two vertical thick plates 81 penetrating the partition plate assembly 8, and can switch the input and output paths of the high-pressure gas flow into and out of the dual-path gas guide valve chamber. It also includes a front-mounted linkage valve 52 connected to the dual-chamber gas distribution valve 51 via a gas guide pipe 53, capable of driving the dual-chamber gas distribution valve 51 to switch its gas guide path. A non-rotatable valve core structure with a rectangular or other polygonal cross-section is provided within the valve body of the dual-chamber gas distribution valve 51. The axial lateral movement of the valve core achieves the alternating conduction and cutoff of the high-pressure gas flow between the two gas guide valve chambers, thereby controlling the periodic deformation of the variable-capacity diaphragm 6. The gas guide pipe 53 uses a high-strength pressure-resistant flexible hose or a rigid metal pipe to ensure the accuracy and timeliness of gas pressure transmission. Simultaneously, a sealing joint is provided at its connection interface to prevent gas leakage from affecting the gas distribution accuracy. The coordinated operation of the dual-chamber air distribution valve 51 and the front-mounted linkage valve 52 provides a stable and adjustable reversing driving force for the variable-capacity diaphragm 6, ensuring the regularity and synchronicity of the change in the volume of the medium guiding valve chamber. It is the core control component for realizing the self-reversing function of the pump drive device.

[0031] like Figure 3 and Figure 5As shown, the dual-chamber gas distribution valve 51 includes a first embedded valve body 511, a first valve core 512, a piston plate 513, and an adjusting connecting pipe head 514. Preferably, the first embedded valve body 511 is embedded in the central gas guide chamber shell 11 such that its two axial ends extend to the outside of the central gas guide chamber shell 11. More preferably, the middle section of the first embedded valve body 511 within the central gas guide chamber shell 11 extends laterally through the two vertical thick plates 81 of the partition plate assembly 8 and into the gas guide valve chamber. Preferably, a first valve core 512, which is a rectangular column capable of changing the flow path of the valve chamber, is slidably inserted into the valve chamber of the first embedded valve body 511. More preferably, piston plates 513, which cooperate with the valve chamber of the first embedded valve body 511 and define two symmetrically arranged variable-capacity adjusting gas chambers, are connected to the axial ends of the first valve core 512. Preferably, both axial ends of the first embedded valve body 511 are also fitted with adjustment connecting pipes 514 that communicate with the variable capacity adjustment gas chamber by welding or integral molding. The adjustment connecting pipes 514 of the dual-chamber gas distribution valve 51 are connected to the corresponding gas ports of the pre-linkage valve 52 through the gas guide pipe 53, thereby receiving the control airflow from the pre-linkage valve 52 and driving the piston plate 513 to drive the first valve core 512 to move axially back and forth within the valve chamber of the first embedded valve body 511. Specifically, when high-pressure control gas is introduced into one side of the adjustment connecting pipe 514, the piston plate 513 on that side pushes the first valve core 512 to move to the other side under the action of gas pressure, so that the guide channel on the first valve core 512 is connected to the gas port of the corresponding gas guide valve chamber on the first embedded valve body 511, while cutting off the connection with the other gas guide valve chamber, thereby realizing the input of high-pressure gas flow to the gas guide valve chamber on that side, driving the corresponding variable capacity diaphragm 6 to deform. Conversely, when the forward linkage valve 52 switches the control airflow direction and introduces high-pressure control gas into the other side adjustment connection pipe head 514, the first valve core 512 moves in the opposite direction, realizing the switching input of high-pressure airflow to the other side gas guide valve chamber, completing the reversal of the gas distribution path. The rectangular column structure design of the first valve core 512 can effectively prevent it from rotating during movement, ensuring precise alignment between the guide channel and the valve body air hole, and guaranteeing the accuracy and reliability of gas distribution. A high-precision seal, such as an O-ring or a combined sealing gasket, is provided between the piston plate 513 and the inner wall of the valve chamber of the first embedded valve body 511 to prevent leakage of control gas in the variable displacement adjustment gas chamber, ensuring that the piston plate 513 can obtain sufficient driving force to drive the first valve core 512 to move stably.

[0032] like Figure 3 and Figure 5As shown, the first embedded valve body 511 has a first air inlet 5111, a second air inlet 5112, a first air outlet 5113, and a second air outlet 5114, which are respectively connected to two non-communicating gas guide valve chambers within the centrally located air guide chamber shell 11 and are staggered in arrangement. More preferably, the first embedded valve body 511 also has a first input port 5115, a second input port 5116, a first output port 5117, and a second output port 5118, respectively, staggered in arrangement on the two end sidewalls extending outside the centrally located air guide chamber shell 11. Specifically, the first air inlet 5111 and the first air outlet 5113 are arranged on the same side, the second air inlet 5112 and the second air outlet 5114 are arranged on the same side, and the distance between the first air inlet 5111 and the first air outlet 5113 is equal to the distance between the second air inlet 5112 and the second air outlet 5114. The first input port 5115 and the first output port 5117 are located on the same side and are respectively located at both ends of the first embedded valve body 511 extending to the outside of the central air guide chamber shell 11. The second input port 5116 and the second output port 5118 are located on the same side and are respectively located at both ends of the first embedded valve body 511 extending to the outside of the central air guide chamber shell 11. Specifically, the first air inlet 5111, the first air outlet 5113, the first input port 5115, the first output port 5117 and the second air inlet 5112, the second air outlet 5114, the second input port 5116, and the second output port 5118 are respectively located on both sides of the first embedded valve body 511. Specifically, the first input port 5115 and the second input port 5116 are connected to a high-pressure gas source through an air inlet pipe with a branched pipeline. Specifically, the first output port 5117 and the second output port 5118 are directly connected to the outside or connected to a gas recovery module through a gas recovery pipeline. Preferably, the valve cylinder of the first embedded valve body 511 is sealed with end caps at both ends, and the adjusting connecting pipe head 514 is inserted into the end caps. Preferably, the first embedded valve body 511 has a sliding groove adapted to the rectangular cross-section of the first valve core 512, and the two ends of the sliding groove have end through grooves that communicate with it, have a cross-section larger than the axial cross-section of the sliding groove, and are adapted to the shape of the surface of the piston plate 513. So when the end cap seals the opening of the end through groove, the part of the end through groove between the piston plate 513 and the end cap forms a variable displacement adjusting gas chamber. Then, by introducing high pressure gas into the variable displacement adjusting gas chamber, the piston plate 513 is pushed to move axially, thereby changing the working position of the first valve core 512 in the first embedded valve body 511. Specifically, the variable-capacity adjusting air chamber is the end valve cavity space of the first embedded valve body 511 that is not filled by the first valve core 512 and is located at both ends of the first valve core 512 along its axial direction. When the air pressure inside the chamber changes, it can push the piston plate 513 to translate, thereby changing the volume inside the chamber and realizing the axial translation drive of the first valve core 512. Specifically, when the first valve core 512 undergoes axial translation, the guide channel opened on its rectangular column will move accordingly, thereby changing the communication relationship with each port on the first embedded valve body 511.For example, when the first valve core 512 moves to a certain position on the left, its flow channel connects the first input port 5115 with the first air inlet 5111, and the second air outlet 5114 with the second output port 5118. At the same time, the first air outlet 5113 is disconnected from the first output port 5117, and the second input port 5116 is disconnected from the second air inlet 5112. At this time, the high-pressure gas flow from the high-pressure gas source enters the corresponding left-side gas flow valve chamber through the first input port 5115, the first air inlet guide groove 5121 of the first valve core 512, and the first air inlet 5111, driving the variable-capacity diaphragm 6 on that side to deform towards the medium flow valve chamber, thus pumping out the medium. Simultaneously, the gas in the right-side gas flow valve chamber is discharged synchronously through the second air outlet 5114, the second exhaust guide groove 5124, and the second output port 5118 connected in sequence, causing the right-side variable-capacity diaphragm 6 to deform towards the gas flow valve chamber, thus pumping in the medium. Conversely, when the first valve core 512 moves to the right to another position, its flow channel switches to connect the second input port 5116 with the second air inlet 5112 and the first air outlet 5113 with the first output port 5117, while simultaneously disconnecting the second air outlet 5114 from the second output port 5118 and the first input port 5115 from the first air inlet 5111. The high-pressure airflow then enters the right gas flow guide valve chamber, driving the right variable displacement diaphragm 6 to deform. The gas in the left gas flow guide valve chamber is discharged through the first air outlet 5113 and the first output port 5117. This alternating switching of the intake and exhaust paths, achieved through the axial translation of the first valve core 512, is the key to the periodic alternating operation of the variable displacement diaphragm 6 controlled by the dual-chamber gas distribution valve 51. The staggered arrangement of the ports on the first embedded valve body 511 and the precise matching with the flow guide channel of the first valve core 512 ensure that there is no crosstalk between the intake and exhaust paths during the movement of the valve core, thus ensuring the accuracy of the air distribution and the stability of the pump drive device.

[0033] Preferably, the first valve core 512 has a first intake guide groove 5121 that connects the first input port 5115 and the first air inlet 5111, a second intake guide groove 5122 that connects the second air inlet 5112 and the second input port 5116, a first exhaust guide groove 5123 that connects the first air outlet 5113 and the first output port 5117, and a second exhaust guide groove 5124 that connects the second air outlet 5114 and the second output port 5118. More preferably, the first intake guide groove 5121 and the first exhaust guide groove 5123 are arranged on the same side, the second intake guide groove 5122 and the second exhaust guide groove 5124 are opened on the same side, and the distance between the first intake guide groove 5121 and the first exhaust guide groove 5123 is equal to the distance between the second intake guide groove 5122 and the second exhaust guide groove 5124. Preferably, the first air intake guide groove 5121, the second air intake guide groove 5122, the first exhaust guide groove 5123, and the second exhaust guide groove 5124 can be open grooves formed on the surface of the first valve core 512, or they can be U-shaped connecting grooves located inside the first valve core 512 with their openings penetrating the side wall of the first valve core 512. Specifically, the open grooves or U-shaped connecting grooves constituting the first air intake guide groove 5121, the second air intake guide groove 5122, the first exhaust guide groove 5123, and the second exhaust guide groove 5124 all have a channel opening cross-section greater than or equal to that of the first air intake port 5111, the first air outlet 5113, the first input port 5115, the first output port 5117, the second air intake port 5112, the second air outlet 5114, the second input port 5116, and the second output port 5118.

[0034] like Figure 2 , Figure 6 and Figure 7As shown, the pre-operated linkage valve 52 includes a second pilot valve body 521, a second linkage valve core 522, a shifting sleeve 523, and a linkage push-pull rod 524. Preferably, the second pilot valve body 521 is detachably mounted on the outward mounting plate 111 of the central air guide chamber shell 11, and the second linkage valve core 522 is axially slidably inserted into the second pilot valve body 521. Specifically, a precision sealing structure is also provided between the second linkage valve core 522 and the inner wall of the second pilot valve body 521 to ensure that no air leakage occurs during air circuit switching, and to ensure the stability and accurate transmission of control air pressure. Preferably, one end of the second linkage valve core 522 is coaxially connected to a shifting sleeve 523 that slides through the second pilot valve body 521. Preferably, a linkage push-pull rod 524 capable of reciprocating translation is also slidably inserted into the shifting sleeve 523. More preferably, one end of the linkage push-pull rod 524 extending to the outside of the shifting sleeve 523 is connected to the transmission assembly 9, causing the linkage push-pull rod 524 to undergo axial reciprocating translation under the push and pull of the transmission assembly 9. The shifting sleeve 523 can provide redundant translation space for the transmission translation of the linkage push-pull rod 524, so that the linkage push-pull rod 524 only pushes the shifting sleeve 523 and the second linkage valve core 522 to switch positions at the end of the unidirectional translation stroke. This avoids the second linkage valve core 522 from malfunctioning due to small vibrations or long displacements of the linkage push-pull rod 524, and improves the operational reliability of the front linkage valve 52. Specifically, when the linkage push-pull rod 524 moves in a certain direction, it first slides freely within the shifting sleeve 523 until its end abuts against the inner wall of the shifting sleeve 523. Only then will the continuing movement of the linkage push-pull rod 524 drive the shifting sleeve 523 and the second linkage valve core 522 to move axially as a whole, realizing the switching of the valve core's position. Conversely, when the linkage push-pull rod 524 moves in the opposite direction, it also first creates a free stroke within the shifting sleeve 523. After its other end abuts against the other inner wall of the shifting sleeve 523, it then drives the whole to move in the opposite direction. This design, by setting a mechanical dead zone, effectively filters out minor disturbances in the transmission process and the ineffective amount of translational movement in the front and middle sections, ensuring that the second linkage valve core 522 only performs the switching action after the linkage push-pull rod 524 has completed the preset stroke, thereby ensuring precise synchronization with the deformation cycle of the variable displacement diaphragm 6.

[0035] The working principle of the pre-operated linkage valve 52 is as follows: When the transmission assembly 9 drives the linkage push-pull rod 524 to move axially, the linkage push-pull rod 524 pushes the shifting sleeve 523 to move synchronously, thereby driving the second linkage valve core 522 to slide within the second pilot valve body 521. The sliding of the second linkage valve core 522 changes its position within the second pilot valve body 521, thereby switching the air guide path between the pre-operated linkage valve 52 and the adjusting connection pipe head 514 of the dual-chamber air distribution valve 51. Specifically, when the linkage push-pull rod 524 moves the second linkage valve core 522 to one side, the pre-linkage valve 52 guides the high-pressure control gas to the adjusting connection pipe head 514 on one side of the dual-chamber gas distribution valve 51, driving the first valve core 512 to move to the other side. When the linkage push-pull rod 524 moves the second linkage valve core 522 in the opposite direction, the pre-linkage valve 52 switches the high-pressure control gas to the adjusting connection pipe head 514 on the other side of the dual-chamber gas distribution valve 51, driving the first valve core 512 to move in the opposite direction. In this way, the pre-linkage valve 52 receives the mechanical displacement signal from the transmission component 9 and converts it into a gas path switching signal, realizing precise control of the valve core position of the dual-chamber gas distribution valve 51, thereby providing a reliable reversing driving force for the periodic deformation of the variable displacement diaphragm 6. The second pilot valve body 521 is provided with a sealing structure that cooperates with the second linkage valve core 522 to ensure that no gas leakage occurs during the gas path switching process, ensuring the stable transmission of control gas pressure. This application directly controls the pre-operated linkage valve 52 through mechanical transmission, avoiding electromagnetic interference, response delay, and dependence on complex control circuits that may result from electrical control methods such as electromagnetic directional valves. It also eliminates feedback lag in signal transmission, significantly improving the anti-interference capability and operational reliability of the pump drive unit in industrial environments. Simultaneously, the directness of the mechanical transmission ensures a high degree of synchronization between the pre-operated linkage valve 52 and the transmission assembly 9, providing a solid guarantee for the precise switching of the dual-chamber air distribution valve 51.

[0036] like Figure 6 and Figure 7As shown, the second linkage valve core 522, driven by the linkage push-pull rod 524, can switch its axial position within the second pilot valve body 521, thereby changing the conduction state of the internal air passage of the second pilot valve body 521. Preferably, an air supply inlet 5211 penetrating its valve housing is provided on the second pilot valve body 521. More preferably, a first air supply outlet 5212 and a second air supply outlet 5213 are also provided on the valve housing of the second pilot valve body 521 on both sides of the air supply inlet 5211. More preferably, two pressure relief ports 5214 are also provided on the valve housing of the second pilot valve body 521. Preferably, the air supply inlet 5211 and the first air supply outlet 5212 and the second air supply outlet 5213 are respectively located on both sides of the second pilot valve body 521; the air supply inlet 5211 and the pressure relief port 5214 are arranged on the same side. Preferably, the pressure relief port 5214 is located on the section of the second pilot valve body 521 located away from the air inlet 5211, where the first air outlet 5212 and the second air outlet 5213 are situated. Preferably, the air inlet 5211 is connected to a high-pressure air source via an air inlet pipe, forming a parallel connection with the first inlet 5115 and the second inlet 5116. Preferably, the first air outlet 5212 and the second air outlet 5213 can be connected to the adjusting connection pipe heads 514 located at both ends of the dual-chamber air distribution valve 51 via two parallel air guide pipes 53, respectively. Annular grooves of different widths and positions are provided on the outer peripheral surface of the second linkage valve core 522. By moving the second linkage valve core 522 axially within the second pilot valve body 521, these annular grooves can change the communication state between the air supply inlet 5211 and the first air supply outlet 5212 and the second air supply outlet 5213, as well as the communication state between the first air supply outlet 5212, the second air supply outlet 5213 and different pressure relief ports 5214. When the linkage push-pull rod 524 moves the second linkage valve core 522 to a certain extreme position, the gas inlet 5211 is connected to the first gas outlet 5212, which serves as the control gas output port, and the second gas outlet 5213 is connected to the pressure relief port 5214. High-pressure gas enters the variable-capacity adjustment gas chamber on the corresponding side of the dual-chamber gas distribution valve 51 through the control gas output port, driving the first valve core 512 to move. Meanwhile, the gas in the variable-capacity adjustment gas chamber on the other side is discharged and depressurized through the pressure relief port 5214. When the linkage push-pull rod 524 moves the second linkage valve core 522 to another extreme position, the gas inlet 5211 is connected to the second gas outlet 5213, which serves as another control gas output port, and the first gas outlet 5212 is connected to the pressure relief port 5214. The high-pressure gas is switched to the variable-capacity adjustment gas chamber on the other side of the dual-chamber gas distribution valve 51, realizing the reverse movement of the first valve core 512. This switching action of the second linkage valve core 522 directly controls the moving direction of the first valve core 512 of the dual-chamber gas distribution valve 51, thereby realizing the alternating input of high-pressure gas flow between the two gas guide valve chambers. It is the "command center" that drives the entire pump drive device to switch directions.

[0037] Preferably, the connection between the linkage push-pull rod 524 and the transmission assembly 9 can be a hinge, a pin, or a rigid connection via a coupling, ensuring that the mechanical motion of the transmission assembly 9 can be accurately transmitted to the linkage push-pull rod 524. The transmission assembly 9, in conjunction with the synchronous horizontal shaft 7, is a mechanism that converts the deformation of the variable displacement diaphragm 6 into linear motion. It can monitor the working position of the variable displacement diaphragm 6 in real time and trigger the reversing action of the linkage push-pull rod 524 when the diaphragm reaches the maximum deformation position, thereby realizing closed-loop linkage control of the working state of the front linkage valve 52 and the variable displacement diaphragm 6. For example, when the left variable displacement diaphragm 6 deforms to its maximum extent towards the medium guide valve chamber, the transmission assembly 9 drives the linkage push-pull rod 524 to move to the right, pushing the second linkage valve core 522 to switch to the right position via the switching sleeve 523, so that the high-pressure airflow switches to the right gas guide valve chamber, driving the right variable displacement diaphragm 6 to start deforming, while the left variable displacement diaphragm 6 resets; and vice versa. This feedback-based commutation control, based on the working state of the variable capacity diaphragm 6, eliminates the need for a complex external electronic control system in the commutation process of the pump drive unit. Instead, it relies entirely on mechanical linkage, which improves the reliability and anti-interference capability of the unit and reduces maintenance costs.

[0038] Preferably, a reinforcing positioning ring 62 is provided at the edge of the diaphragm body 61 of the variable displacement diaphragm 6, which is snapped between the expansion chamber shell 12 and the medium guide tube shell 13. Preferably, a connecting seat 63 is also integrally formed at the center of the surface of the diaphragm body 61 facing the central gas guide chamber shell 11. Preferably, the connecting seat 63 is connected to the axial end of the synchronous horizontal shaft 7 through a rotary connector inserted into its seat body. The diaphragm body 61 is made of fluororubber or nitrile rubber material with high elasticity and resistance to media corrosion. It consists of at least two layers of stacked material, with a single layer thickness of 3-5 mm, ensuring good elastic recovery performance and structural stability during high-frequency deformation. This ensures sufficient deformation under gas pressure and maintains good elastic recovery performance during high-frequency deformation, achieving effective pumping of the medium and ensuring structural strength and service life under long-term reciprocating deformation. The reinforced positioning ring 62 further enhances the sealing performance, installation firmness, and rigidity of the diaphragm body 61 edge, effectively preventing edge tearing or displacement during assembly and operation. It also forms a reliable sealing boundary through a tight fit with the expansion cavity shell 12 and the medium guide tube shell 13, effectively preventing leakage of medium or gas from the cavity edge. The integral molding design of the connecting seat 63 and the diaphragm body 61 avoids stress concentration and leakage risks that may arise from adhesive or mechanical connections, ensuring that the deformation of the diaphragm body 61 can be accurately and efficiently transmitted to the synchronous horizontal shaft 7, providing reliable power input for the subsequent operation of the transmission assembly 9, and guaranteeing the smoothness and accuracy of the mechanical transmission. The rotating connector allows the diaphragm body 61 to undergo a certain angular deflection during deformation and enables a detachable connection between the connecting seat 63 and the synchronous horizontal shaft 7, avoiding the additional torque generated by the rigid connection between the synchronous horizontal shaft 7 and the connecting seat 63, further protecting the connection structure between the diaphragm body 61 and the synchronous horizontal shaft 7.

[0039] like Figure 4As shown, a rolling groove 71 parallel to the axis of the synchronous horizontal shaft 7 is formed on the shaft wall. Specifically, the cross-sectional profile of the rolling groove 71 is an arc that matches the annular surface of the rolling drive wheel 91. Preferably, the synchronous horizontal shaft 7 is a shaft with a rectangular cross-section, and both ends of the shaft are provided with rod heads that match the rotary connector. The rotary connector and the rod heads at the ends of the synchronous horizontal shaft 7 are circumferentially fixed by a key or spline connection, ensuring that the reciprocating linear motion of the diaphragm body 61 can be stably converted into the axial translation of the synchronous horizontal shaft 7, effectively transmitting the driving torque of the diaphragm body 61, so that the synchronous horizontal shaft 7 can move axially strictly according to the deformation rhythm of the diaphragm body 61, providing a stable mechanical synchronization guarantee for the coordinated operation of the entire pump drive device. The rolling groove 71 extends along the length of the synchronous horizontal shaft 7, and its number can be set to one or more according to the transmission requirements. The depth and width of the rolling groove 71 are precisely designed based on the transmission load and the dimensional parameters of the rolling transmission wheel 91. Typically, the groove depth is 1 / 4 to 1 / 5 of the wall thickness of the synchronous horizontal shaft 7, and the groove width is 0.5-1 mm larger than the wheel width of the rolling transmission wheel 91. This ensures that the rim of the rolling transmission wheel 91 can form good line contact with the groove wall, reducing friction and wear during transmission, while also ensuring transmission accuracy and preventing slippage. This ensures that the rolling transmission wheel 91 can roll smoothly within the groove without axial movement. The surface of the rolling groove 71 is precision ground, with a surface roughness profile arithmetic mean deviation not exceeding 0.8 μm. While ensuring roll transmission without relative slippage, this appropriately reduces the coefficient of friction between the groove and the rolling transmission wheel 91, reducing energy loss and component wear during transmission, and ensuring that the axial translational movement of the synchronous horizontal shaft 7 can be efficiently and smoothly transmitted to the transmission assembly 9. The rectangular cross-section design of the shaft provides the synchronous horizontal shaft 7 with good bending stiffness and torsional strength, preventing bending or torsional deformation during reciprocating motion and ensuring the accuracy and stability of the transmission. Compared with the traditional circular cross-section, the rectangular cross-section design of the synchronous horizontal shaft 7 can better match the guide structure on which it is installed, preventing circumferential rotation of the synchronous horizontal shaft 7 during axial movement. This ensures that the relative position between the rolling groove 71 and the rolling transmission wheel 91 remains constant, providing guidance for the stable operation of the transmission assembly 9. The synchronous horizontal shaft 7 is preferably made of high-strength alloy steel, such as a combination of quenched steel and hardened cast iron. After tempering treatment, its overall structural strength and fatigue resistance are improved, effectively suppressing the tendency to slip and meeting the requirements of long-term, high-frequency reciprocating motion.

[0040] Preferably, the partition plate assembly 8 includes two parallel vertical thick plates 81 and bolts 82 connecting the two vertical thick plates 81. More preferably, the two vertical thick plates 81 are symmetrically embedded in the central gas guide chamber shell 11, and the circumferentially spaced bolts 82 tighten and limit the relative position between the two vertical thick plates 81 by passing through them, so that the two vertical thick plates 81 divide the central gas guide chamber shell 11 into three sections. Thus, the two end chambers of the central gas guide chamber shell 11 form gas flow valve chambers, and the middle section valve chamber between the two vertical thick plates 81 forms a central chamber that accommodates the dual-chamber gas distribution valve 51, transmission assembly 9, and other structures. Specifically, the dual-path gas flow valve chambers are two symmetrically arranged and parallel local chambers of the central gas guide chamber shell 11 located between the variable-capacity diaphragm 6 and the vertical thick plates 81, which define two mutually isolated high-pressure gas channels.

[0041] like Figure 1 and Figure 4 As shown, a through hole 811 for slidingly inserting the synchronous horizontal shaft 7 is provided at the center of the vertically placed thick plate 81. Preferably, multiple sliding sealing rings 812 are spaced apart along the axial direction of the through hole 811, forming a dynamic seal by filling the assembly gap between the cavity and the synchronous horizontal shaft 7. Preferably, the sliding sealing rings 812 include various sealing components such as rubber sealing rings and graphite sealing rings. More preferably, a sealing protrusion 813 is integrally formed on the radially inner side of the sliding sealing ring 812. Preferably, the sealing protrusion 813 can adaptively seal and fill the rolling groove 71 of the synchronous horizontal shaft 7, forming an effective sealing isolation. More preferably, a shaft floating seal composed of multiple sealing rings, separator rings, support rings, and oil seals can also be provided in the through hole 811 to form a multi-stage seal and share the pressure difference. like Figure 2As shown, the transmission assembly 9 includes a rolling transmission wheel 91, a transmission shaft 92, a rotating screw 93, a transmission nut 94, a guide slider 95, and a guide rail 96. Preferably, the rolling transmission wheel 91 is mounted on the transmission shaft 92, and the transmission shaft 92 is rotatably inserted into the central air guide chamber shell 11 located between two vertical thick plates 81, such that the rolling transmission wheel 91 is in transmission rolling contact with the portion of the synchronous horizontal shaft 7 located between the two vertical thick plates 81 through the rolling groove 71 partially located on the synchronous horizontal shaft 7. Preferably, the transmission shaft 92 passes through the central air guide chamber shell 11 and extends to one end coaxially connected to the rotating screw 93 on the outside of the central air guide chamber shell 11, and a transmission nut 94 is mounted on the rotating screw 93. Preferably, the end of the rotating screw 93 away from the transmission shaft 92 is also rotatably mounted with a bearing support seat supported on the outward mounting plate 111. Preferably, the guide rail 96 is mounted on the outward mounting plate 111 in a manner parallel to the rotating screw 93. More preferably, a guide slider 95, fitted onto the transmission nut 94, is slidably mounted within the groove of the guide rail 96. This guide slider 95, whose sliding direction is defined by the guide rail 96, can limit the movable direction of the transmission nut 94, thereby enabling the transmission nut 94 to synchronously translate axially when the rotating screw 93 rotates around its axis. The transmission nut 94 then drives the guide slider 95 to translate synchronously. Preferably, the guide slider 95 is also connected to the end of the linkage push-pull rod 524 away from the second pilot valve body 521, in a manner that drives the linkage push-pull rod 524 to synchronously reciprocate axially. Specifically, the side of the guide slider 95 is detachably connected to the linkage push-pull rod 524 via a connecting plate seat and a fitted limit bolt. Specifically, the rolling connection between the rolling drive wheel 91 and the synchronous horizontal shaft 7 refers to a moving connection characterized by instantaneous line contact and single-degree-of-freedom constraint, which is categorized as a line contact translation-rolling linkage. Preferably, a rolling wheel sleeve made of a high-elasticity modulus material, such as tungsten carbide, is fitted onto the central wheel body of the rolling drive wheel 91. Specifically, the surface of the rolling wheel sleeve of the rolling drive wheel 91 needs to be hardened, such as by carburizing or diamond coating, to reduce sliding errors caused by wear. Furthermore, the contact pressure between the rolling drive wheel 91 and the synchronous horizontal shaft 7 can be increased by applying a preload, thereby effectively suppressing slippage.

[0042] This invention is not limited to the above-described optional embodiments. Anyone inspired by this invention can derive various other forms of products. Regardless of any changes in shape or structure, any technical solution falling within the scope of the claims is protected by this invention. Those skilled in the art should understand that this specification and its accompanying drawings are illustrative and not intended to limit the scope of the claims. The scope of protection of this invention is defined by the claims and their equivalents. Throughout the text, features introduced by "preferred" are merely optional and should not be construed as mandatory. Therefore, the applicant reserves the right to abandon or delete relevant preferred features at any time.

Claims

1. A self-reversing pump drive device for stabilizing the flow of soldering flux in liquid-cooled plate processing, comprising a valve housing (1), characterized in that, At both ends of the valve housing (1) are respectively connected a diversion input pipe (2) and a confluence output pipe (3) that can communicate with the medium guiding valve chamber. A linkage gas distribution valve group (5) is also provided on the valve housing (1) that penetrates the partition plate group (8) and selectively communicates with two parallel gas guiding valve chambers. The linkage gas distribution valve group (5) can switch the input and output paths of the high-pressure gas flow into and out of the gas guiding valve chamber in conjunction with the working state of the variable displacement diaphragm (6). The central air guide chamber shell (11) of the valve shell (1) is divided into two symmetrically distributed local shell cavities by the vertical thick plate (81) of the partition plate group (8), which are gas guide valve cavities. The extended cavity shell (12) of the valve shell (1) and the medium guide pipe shell (13) together define the medium guide valve cavity. The two variable capacity diaphragms (6) are arranged in a way that separates the medium flow valve chamber from the gas flow valve chamber at both ends of the central gas guide chamber shell (11). The two variable capacity diaphragms (6) are linked together by a synchronous horizontal shaft (7), and the synchronous horizontal shaft (7) is slidably inserted into the through hole (811) of the vertical thick plate (81). The linked air distribution valve group (5) is connected to the synchronous horizontal shaft (7) that undergoes continuous reciprocating lateral movement via a transmission component (9) that passes through the valve housing (1).

2. The self-reversing pump drive device for stable flow supply of brazing flux for liquid-cooled plate processing as described in claim 1, characterized in that, Extended chamber shells (12) are symmetrically arranged on both sides of the centrally located air guide chamber shell (11), and a medium guide tube shell (13) is also connected to the side of the extended chamber shell (12) away from the centrally located air guide chamber shell (11). The variable-capacity diaphragm (6) is sandwiched between the centrally located air guide cavity shell (11) and the extended cavity shell (12); The partition plate assembly (8) is installed in the center of the centrally located gas guide chamber shell (11) in such a way that it is divided into two symmetrically arranged gas guide valve chambers.

3. The self-reversing pump drive device for stable flow supply of brazing flux for liquid-cooled plate processing as described in claim 2, characterized in that, The linkage gas distribution valve group (5) includes a dual-chamber gas distribution valve (51) which is embedded in the central gas guide chamber shell (11) in a manner that penetrates the partition plate group (8) and can switch the input path and output path of the high-pressure gas flow into and out of the dual-path gas guide valve chamber, and a front linkage valve (52) which is connected to the dual-chamber gas distribution valve (51) through the gas guide pipe (53) and can drive the dual-chamber gas distribution valve (51) to switch the gas guide path.

4. The self-reversing pump drive device for stable flow supply of soldering flux for liquid-cooled plate processing as described in claim 3, characterized in that, The first embedded valve body (511) of the dual-chamber gas distribution valve (51) is embedded in the centrally located air guide chamber shell (11); a first valve core (512) is slidably inserted in the valve chamber of the first embedded valve body (511), and piston plates (513) that cooperate with the valve chamber of the first embedded valve body (511) to define two symmetrically arranged variable-capacity adjusting gas chambers are connected to the axial ends of the first valve core (512); adjusting connecting pipe heads (514) that communicate with the variable-capacity adjusting gas chambers are also inserted at the axial ends of the first embedded valve body (511).

5. The self-commutating pump drive device for stable flow supply of brazing flux for liquid-cooled plate processing as described in claim 4, characterized in that, The second pilot valve body (521) of the pre-connected linkage valve (52) is detachably mounted on the outward mounting plate (111) of the central air guide chamber shell (11), and a second linkage valve core (522) is axially slidably inserted in the second pilot valve body (521); a shifting sleeve (523) that slides through the second pilot valve body (521) is coaxially connected to one end of the second linkage valve core (522), and a linkage push-pull rod (524) is also slidably inserted in the shifting sleeve (523).

6. The self-commutating pump drive device for stable flow supply of brazing flux for liquid-cooled plate processing as described in claim 5, characterized in that, The rolling drive wheel (91) of the transmission assembly (9) is mounted on the transmission shaft (92), and the transmission shaft (92) is rotatably inserted into the central air guide chamber shell (11), so that the rolling drive wheel (91) is in transmission rolling contact with the synchronous horizontal shaft (7).

7. The self-commutating pump drive device for stable flow supply of brazing flux for liquid-cooled plate processing as described in claim 6, characterized in that, The transmission shaft (92) extends to one end of the outer side of the central air guide chamber shell (11) and is coaxially connected to a rotating screw (93), and a transmission nut (94) is fitted on the rotating screw (93). The guide rail (96) of the transmission assembly (9) is mounted on the outward mounting plate (111), and a guide slider (95) fitted on the transmission nut (94) is also slidably mounted in the groove of the guide rail (96). The guide slider (95) is also connected to the end of the linkage push-pull rod (524) away from the second pilot valve body (521).

8. The self-reversing pump drive device for stabilizing the flow of soldering flux for liquid-cooled plate processing as described in claim 7, characterized in that, An adaptive flow stabilizing component (4) is inserted into the shell wall of the medium guide tube shell (13), and the linkage tube (41) is also connected to the flow stabilizing regulating tube (43) inserted into the outflow branch pipe (31) of the confluence output pipe (3) through an external equivalent pipeline (42).

9. The self-commutating pump drive device for stable flow supply of soldering flux for liquid-cooled plate processing as described in claim 8, characterized in that, The first shell (411) of the linkage tube (41) is inserted into the shell wall of the medium guide tube shell (13), and a first piston body (412) capable of variable volume separation of its cavity is provided inside the first shell (411); the closed end of the linkage tube (41) is also slidably inserted with a limiting slide rod (413) capable of limiting the translational distance of the first piston body (412), and a connecting tube (414) connected to the axial end face of the first shell (411) is also fitted on the limiting slide rod (413).

10. The self-reversing pump drive device for stable flow supply of soldering flux for liquid-cooled plate processing as described in claim 9, characterized in that, The flow regulating tube (43) includes a second shell (431) inserted into the side wall of the outflow branch pipe (31), a second piston body (432) disposed in the second shell (431), and a flow limiting column (433) connected to the second piston body (432) and capable of changing the flow guiding cross-section size of the outflow branch pipe (31) by partially moving into the outflow branch pipe (31). The end of the second piston body (432) away from the flow-limiting column (433) is also connected to an elastic limiting spring (434) that limits its initial position in the second cylinder (431).

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