Four-cylinder single-acting high-pressure diaphragm pump

Abstract

This invention relates to a four-cylinder single-acting high-pressure diaphragm pump, belonging to the technical field of fluid transport equipment. The power end of the invention includes a crankshaft, a housing, and a linkage mechanism. The crankshaft has a four-crank structure. The hydraulic end includes four diaphragm chambers. Each diaphragm chamber is connected to and communicates with the housing of the power end via a cavity and a cylinder. The inlet and outlet of each diaphragm chamber are directly connected to a feed valve box and a discharge valve box, respectively. Two feed valve boxes share a feed pipe, and the other two feed valve boxes share another feed pipe. Two discharge valve boxes share a discharge pipe, and the other two discharge valve boxes share another discharge pipe. The two discharge pipes are independent of each other, and a discharge compensation device is provided at the discharge port of each discharge pipe. The two discharge compensation devices form a parallel arrangement. This invention solves the problem in the prior art that it is impossible to achieve two independent outputs with highly consistent pressure and flow rates and low pulsation with a single device.

Description

Technical Field

[0001] This invention belongs to the field of fluid transport equipment technology, and specifically relates to a four-cylinder single-acting high-pressure diaphragm pump. Background Technology

[0002] The four-nozzle opposed-position coal-water slurry gasification process has become the preferred process for large-scale coal chemical projects due to its advantages such as high carbon conversion rate and wide adaptability of raw materials. This process requires supporting conveying equipment to provide two independent high-pressure media with highly consistent flow and pressure and extremely low pressure pulsation for the two sets of opposed nozzles.

[0003] Currently, high-pressure diaphragm pumps suitable for this operating condition have the following main shortcomings: First, under high-pressure conveying conditions, the sealing components of existing double-cylinder double-acting diaphragm pumps are subjected to large alternating loads, making them prone to seal failure and media leakage. Their operational reliability and service life are insufficient to meet the demands of long-term continuous production. Second, the scheme of using two three-cylinder single-acting diaphragm pumps in parallel for material supply suffers from high equipment investment costs, large footprint, and a significant increase in spare parts inventory. Furthermore, the multi-pump linkage complicates the transmission structure, leading to a high system failure rate and making it difficult to guarantee operational coordination and overall reliability. Summary of the Invention

[0004] This invention addresses the aforementioned problems and overcomes the shortcomings of existing technologies by providing a four-cylinder single-acting high-pressure diaphragm pump. This invention solves the problem in existing technologies that it is impossible to achieve highly consistent pressure and flow rates with low pulsation independent output from two separate devices using a single unit.

[0005] To achieve the above objectives, the present invention adopts the following technical solution.

[0006] This invention provides a four-cylinder single-acting high-pressure diaphragm pump, comprising a power transmission system, a power end connected to and driven by the power transmission system, and a hydraulic end connected to the power end. The power end comprises a crankshaft, a housing, and linkage mechanisms. The crankshaft is connected to the housing via multiple support bearings and to the power transmission system via a coupling. The crankshaft has a four-crank structure, with one linkage mechanism connected to each crank. The four linkage mechanisms are respectively connected to piston rods of four pistons fixed within the edge of the housing. The hydraulic end comprises four diaphragm chambers, each of which is connected and communicates with the housing of the power end via a cavity and a cylinder. The piston body of the piston can perform reciprocating linear motion, driving the diaphragm in the diaphragm chamber to undergo elastic deformation, causing the internal volume of the diaphragm chamber to periodically increase and decrease. The inlet and outlet of each diaphragm chamber are directly connected to a feed valve box and a discharge valve box, respectively. Two feed valve boxes are connected to a feed pipe, and two other feed valve boxes are connected to another feed pipe. The two feed pipes are connected to the feed source after passing through a feed compensation device. Two discharge valve boxes are connected to a discharge pipe, and two other discharge valve boxes are connected to another discharge pipe. The two discharge pipes are independent of each other, and a discharge compensation device is provided at the discharge port of each discharge pipe. The two discharge compensation devices form a parallel arrangement structure.

[0007] Furthermore, the four cranks of the crankshaft, from the direction closest to the coupling of the power transmission system to the direction furthest away, are respectively the first crank, the second crank, the third crank, and the fourth crank. Each pair of adjacent cranks is connected by a curved streamline transition crank arm. The phase angle between the first crank and the second crank is 180°, the phase angle between the third crank and the fourth crank is 180°, and the phase angle between the second crank and the third crank is 90°. The first crank and the second crank share the same working unit at the hydraulic end of one discharge pipe, and the third crank and the fourth crank share another working unit at the hydraulic end of another discharge pipe.

[0008] Furthermore, the linkage mechanism includes a connecting rod, a crosshead, and a median rod. The connecting rod is connected to the crank, and the crosshead is connected to the end of the connecting rod via a pin bearing. The crosshead reciprocates along the inside of a guide plate provided in the housing. The median rod is connected to the end of the crosshead and is fixedly connected to the piston rod via a clamp.

[0009] Furthermore, the crankshaft is connected to the housing via three support bearings, which are respectively located at both ends and the middle of the crankshaft.

[0010] Furthermore, the valves in both the feed valve box and the discharge valve box are cone valves, and the valve box bodies are all made of castings.

[0011] Furthermore, the discharge compensation device is a nitrogen tank to attenuate the pressure pulsation of the two discharge pipelines.

[0012] Furthermore, the nitrogen tank is filled with gas at a pressure of 0.4 to 0.65 times the working pressure.

[0013] The beneficial effects of the present invention.

[0014] This invention enables dual-path independent high-pressure output from a single unit, directly replacing the traditional parallel configuration of two three-cylinder diaphragm pumps. This significantly reduces equipment investment costs, floor space, and spare parts inventory. The two cylinders corresponding to the same discharge port operate alternately with a 180° phase difference, ensuring continuous and stable output without flow interruptions or significant fluctuations. The four crankshafts are arranged with a 90° phase difference, resulting in uniform starting torque, minimal operational impact, and significantly improved operational stability and reliability. The dual independent discharge ports correspond to two sets of opposed nozzles in the gasifier, ensuring naturally synchronized and consistent outlet pressure and flow, fully meeting the core requirements of the four-nozzle opposed gasification process for pressure equalization and flow stabilization in the feeding system. Both discharge ports are equipped with nitrogen tanks for independent pulsation attenuation, controlling pressure pulsation amplitude to an extremely low level, effectively reducing pipeline vibration and valve erosion, and extending system lifespan. Attached Figure Description

[0015] To make the technical problems solved, the technical solutions, and the beneficial effects of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0016] Figure 1 This is a schematic diagram of the overall front view of the present invention.

[0017] Figure 2 This is a top view schematic diagram of the overall structure of the present invention.

[0018] Figure 3 This is a cross-sectional structural diagram of the power end of the present invention.

[0019] Figure 4 This is a schematic diagram of the crankshaft structure of the present invention.

[0020] Figure 5 This is the invention Figure 4 A schematic diagram of the crankshaft structure from direction A.

[0021] Figure 6 This is a side view of the hydraulic end of the present invention.

[0022] Figure 7 This is a top view of the hydraulic end of the present invention after the discharge compensation device has been removed.

[0023] The markings in the diagram are as follows: 1 is the power transmission system, 2 is the power end, 3 is the hydraulic end, 4 is the crankshaft, 5 is the housing, 6 is the support bearing, 7 is the piston rod, 8 is the piston body, 9 is the diaphragm chamber, 10 is the cavity and cylinder, 11 is the feed valve box, 12 is the discharge valve box, 13 is the feed pipe, 14 is the feed compensation device, 15 is the discharge pipe, 16 is the discharge compensation device, 17 is the first crank, 18 is the second crank, 19 is the third crank, 20 is the fourth crank, 21 is the crank arm, 22 is the connecting rod, 23 is the crosshead, 24 is the connecting rod, 25 is the pin bearing, 26 is the guide plate, and 27 is the clamp. Detailed Implementation

[0024] Combined with appendix Figure 1 and 2 As shown, this embodiment provides a four-cylinder single-acting high-pressure diaphragm pump, mainly comprising three parts: a power transmission system 1, a power end 2, and a hydraulic end 3. The entire unit is horizontally arranged. The output end of the power transmission system 1 is connected to the input end of the crankshaft 4 of the power end 2 via a coupling. The power end 2 is connected to the cavity and cylinder 10 of the hydraulic end 3. The power transmission system 1 provides power input to the entire diaphragm pump, the hydraulic end 3 is used to complete the suction, pressurization, and discharge of the slurry, and the power end 2 is used to convert the rotational motion of the power transmission system 1 into linear reciprocating motion to drive the hydraulic end 3.

[0025] The power transmission system 1 is the power input unit of this invention, including a main motor and a reducer. The output shaft of the main motor is connected to the input shaft of the reducer, and the output shaft of the reducer is connected to the input end of the crankshaft 4 of the power end 2 via a coupling. During operation, the main motor starts, and after the speed is reduced and the torque is increased by the reducer, it drives the crankshaft 4 to rotate. This power transmission system 1 has high transmission efficiency and stable torque output, which can meet the power requirements under high-pressure conditions. It also has low operating noise and low vibration, providing power assurance for the long-term stable operation of the equipment. The specific selection and parameter design of the power transmission system 1 are well known in the art and will not be described in detail here.

[0026] As attached Figure 3As shown, the power end 2 is the core motion conversion component of this invention, including a crankshaft 4, a housing 5, and a linkage mechanism composed of a connecting rod 22, a crosshead 23, and a connecting rod 24. The housing 5 is constructed from welded sheet metal, and stress relief treatment is performed after welding to eliminate residual welding stress. A guide plate 26 is provided inside the housing 5 to guide the reciprocating motion of the crosshead 23. Inspection holes are provided on both sides of the housing 5 corresponding to the piston rod 7, the crosshead 23, and the guide plate 26, respectively, to facilitate daily inspection and maintenance of the equipment. All pressure-bearing and critical load-bearing components have undergone finite element strength and stiffness verification to ensure stable operation of each component under high pressure and alternating load conditions.

[0027] As attached Figure 4 and 5 As shown, the crankshaft 4 adopts a four-crank, three-support structure, connected to the housing 5 by three support bearings 6. The three support bearings 6 are respectively located at both ends and the middle of the crankshaft 4. The support bearings 6 are preferably self-aligning roller bearings, which can realize automatic adjustment and positioning. The three-support structure significantly improves the overall rigidity and centering of the crankshaft 4, effectively avoids off-center vibration caused by the bending deformation of the crankshaft 4 during operation, reduces the wear rate of moving pairs such as connecting rod 22 and crosshead 23, and extends the service life of key moving parts. The four cranks of the crankshaft 4, from the direction closest to the coupling of the power transmission system 1 to the direction furthest away, are the first crank 17, the second crank 18, the third crank 19, and the fourth crank 20, respectively. The two adjacent cranks are connected by a curved streamline transition crank arm 21. Compared with the traditional straight crank arm, the curved streamline transition structure increases the fillet transition radius, effectively avoids stress concentration, significantly reduces the stress level at the root of the crank arm 21 under alternating loads, and greatly improves the fatigue resistance of the crankshaft 4.

[0028] The phase arrangement of crankshaft 4 is one of the core innovations of this invention. The phase angle between the first crank 17 and the second crank 18 is 180°, the phase angle between the third crank 19 and the fourth crank 20 is 180°, and the phase angle between the second crank 18 and the third crank 19 is 90°. The first crank 17 and the second crank 18 together correspond to the working unit in the hydraulic end 3 that is connected to the same discharge pipe 15; the third crank 19 and the fourth crank 20 correspond to another working unit in the hydraulic end 3 that is connected to another discharge pipe 15. The two cranks corresponding to the same discharge pipe 15 drive the corresponding two cylinders to work alternately with a 180° phase difference. When one cylinder is performing the discharge stroke, the other cylinder is performing the suction stroke. The two cylinders alternately and continuously perform work, so that the discharge pipe 15 always maintains a continuous and stable output, and the flow rate is maintained in a stable range without obvious interruption or large fluctuation. Meanwhile, the 90° phase angle arrangement between the second crank 18 and the third crank 19 makes the driving torque distribution more uniform within the 360° rotation cycle of the whole machine, which can provide a continuous and stable driving torque for the crosshead 23. This effectively avoids problems such as difficulty in starting the equipment, increased impact load and fatigue damage of components caused by uneven phase, and significantly improves the operational reliability and service life of the equipment.

[0029] The linkage mechanism converts the rotational motion of the crankshaft 4 into linear reciprocating motion. The large end of the connecting rod 22 is connected to the crankshaft, and the small end of the connecting rod 22 is connected to the crosshead 23 via a pin bearing 25. The crosshead 23 is located inside the guide plate 26 of the housing 5 and slides reciprocally along the guide plate 26. Sufficient cooling and lubricating fluid is continuously supplied to the housing 5 to ensure stable operation of the crosshead 23 and reduce friction and wear. The intermediate rod 24 is connected to the end of the crosshead 23 and is fixed and locked to the piston rod 7 by a clamp 27. This clamp 27 connection method facilitates the installation, disassembly, and maintenance of the equipment. When the crankshaft 4 rotates, the connecting rod 22 swings due to the eccentricity, which drives the crosshead 23, intermediate rod 24, and piston rod 7 to perform reciprocating linear motion, thereby driving the piston body 8 of the hydraulic end 3 to reciprocate within the cavity and cylinder 10. The moving parts, such as the connecting rod 22, crosshead 23, and intermediate rod 24, are formed by casting and forging processes, which take into account both structural strength and machinability, and further improve the overall reliability of the power end 2.

[0030] As attached Figure 6 and 7As shown, the hydraulic end 3 is the core component of this invention for realizing the functions of slurry pressurization and conveying. It includes four diaphragm chambers 9, four cavities and cylinders 10, four feed valve boxes 11, four discharge valve boxes 12, two feed pipes 13, two discharge pipes 15, a feed compensation device 14, and a discharge compensation device 16. The four diaphragm chambers 9 are arranged in parallel, and each diaphragm chamber 9 is connected and communicated with the housing 5 of the power end 2 through a cavity and cylinder 10. Specifically, the right end of the cavity and cylinder 10 is fixedly connected to the housing 5 of the power end 2, and the left side is fastened to the diaphragm chamber 9 through a positioning stop bolt. This positioning stop bolt connection method ensures the alignment accuracy and connection reliability between the cavity and cylinder 10 and the diaphragm chamber 9. The piston body 8 is located inside the cavity and cylinder 10. The extended end of the piston rod 7 extends into the cavity and cylinder 10 and is fixedly connected to the piston body 8. The piston body 8 is equipped with a piston seal to ensure the sealing performance of the piston body 8 during reciprocating motion and prevent hydraulic oil leakage. When the piston rod 7 drives the piston body 8 to perform reciprocating linear motion, the piston body 8, through the hydraulic oil in the cavity and cylinder 10, drives the diaphragm in the diaphragm chamber 9 to undergo elastic deformation, causing the internal volume of the diaphragm chamber to periodically increase and decrease. The diaphragm is made of corrosion-resistant rubber to adapt to high-pressure and corrosive media conditions. When the diaphragm chamber volume increases, the internal pressure decreases, the feed valve opens, and the discharge valve closes. The external slurry is drawn into the diaphragm chamber under atmospheric pressure or feed pressure, completing the media intake. When the diaphragm chamber volume decreases, the internal pressure increases, the feed valve closes, and the discharge valve opens. The slurry in the diaphragm chamber is pressurized and discharged through the discharge valve box 12, completing the media discharge. By periodically changing the volume of the diaphragm cavity, the inlet and outlet valves are opened and closed alternately, achieving continuous and stable delivery of the medium. The diaphragm completely isolates the hydraulic oil from the conveyed slurry, preventing the piston seal from directly contacting the high-solids-content and highly corrosive medium, thus greatly improving the operational stability of the equipment under harsh working conditions.

[0031] Each diaphragm chamber 9 has its inlet directly connected to a feed valve box 11 and its outlet directly connected to a discharge valve box 12. The valves in both the feed valve box 11 and the discharge valve box 12 are cone valves, with the valve box body made of casting, providing excellent wear resistance and erosion resistance. Compared to traditional ball valves or flat valves, the cone valve structure offers better sealing and erosion resistance, making it particularly suitable for conveying slurries with high solids content and high flow rates. The feed channel adopts a direct-connection, straight-through arrangement, meaning the feed valve box 11 is directly connected to the inlet of the diaphragm chamber 9 without any bends or transition sections. This straight-through channel design simplifies the channel structure, reduces the slurry retention area within the channel, effectively lowers flow resistance, and avoids slurry deposition and blockage caused by abrupt changes in channel cross-section or drastic changes in flow direction. This significantly improves the equipment's adaptability to high solids content and high viscosity slurry media. The diaphragm chamber 9 is connected to the feed valve box 11 and the discharge valve box 12 by a flange sealing structure, which ensures the sealing reliability of the connection and facilitates the disassembly, maintenance and replacement of vulnerable parts of the valve box.

[0032] The four diaphragm chambers 9 are divided into two groups according to their discharge relationship: the discharge valve boxes 12 of two diaphragm chambers 9 are connected to a common discharge pipe 15, and the discharge valve boxes 12 of the other two diaphragm chambers 9 are connected to a common discharge pipe 15. The two discharge pipes 15 are independent of each other and do not intersect, each forming an independent high-pressure slurry conveying channel. Correspondingly, the two feed valve boxes 11 are connected to a common feed pipe 13, and the other two feed valve boxes 11 are connected to a common feed pipe 13. The two feed pipes 13 are connected to the feed source after passing through the feed compensation device 14. The feed compensation device 14 is used to stabilize the pressure of the feed pipeline, ensure uniform intake of each cylinder, and prevent inconsistent intake of each cylinder due to pressure fluctuations in the feed pipeline.

[0033] The two cylinders corresponding to the first crank 17 and the second crank 18 (including the piston body 8, the cavity and the oil cylinder 10, the diaphragm chamber 9 and the related valve box) share the same discharge pipe 15, forming an independent conveying unit; the two cylinders corresponding to the third crank 19 and the fourth crank 20 share another discharge pipe 15, forming another independent conveying unit. Since the two cylinders corresponding to the same discharge pipe 15 are driven by two cranks with a phase angle of 180°, the two cylinders alternately perform the discharge stroke and the suction stroke. When one cylinder is in the discharge stroke, the other cylinder is in the suction stroke. The two cylinders alternately and continuously perform work, so that the discharge pipe 15 always maintains a continuous and stable output, and the flow rate is maintained in a stable range without obvious interruption or large fluctuation. The two independent conveying units are driven by the same crankshaft 4, and there is a 90° phase difference between the two units. This ensures that the high-pressure slurry output from the two discharge pipes 15 naturally maintains a high degree of consistency and synchronicity in pressure and flow. It can be directly connected to the two opposing nozzles of the four-nozzle gasifier to achieve symmetrical feeding and fully meet the stringent requirements of the four-nozzle gasification process for high consistency of flow and pressure in the two opposing nozzle pipelines.

[0034] The discharge compensation device 16 installed on the discharge pipe 15 is one of the core innovations of this invention. Each of the two discharge pipes 15 has a discharge compensation device 16 installed at its discharge port, forming a parallel arrangement. The discharge compensation device 16 is a nitrogen tank, used to absorb and buffer pressure pulsations in the discharge pipeline, attenuating pressure fluctuations in both discharge pipelines. Each discharge pipe 15 is independently equipped with a nitrogen tank, allowing both pipelines to attenuate pulsations simultaneously without interference, ensuring that pressure pulsations in both discharge pipelines are effectively suppressed. The preferred filling pressure of the nitrogen tank is 0.4 to 0.65 times the working pressure. By setting the filling pressure within this range, the nitrogen in the nitrogen tank can effectively absorb and release energy during pressure pulsations, achieving a good buffering effect on pressure fluctuations in the pipeline. This avoids insufficient buffering capacity due to excessively low filling pressure, and also prevents the nitrogen tank from becoming too stiff and losing its pulsation absorption effect due to excessively high filling pressure. The volume of the nitrogen tank is precisely calculated based on the flow rate, pressure pulsation frequency, and amplitude of the slurry in the pipeline, ensuring that the buffering capacity of the nitrogen tank matches the pulsation characteristics within the pipeline. The specific calculation methods and selection are well-known techniques in the field, and those skilled in the art can determine them based on actual operating parameters. The nitrogen tank inlet adopts a small-diameter, short-length, tapered structure and is installed close to the outlet. The inner diameter of the inlet connecting pipe is preferably 1 / 4 to 1 / 2 of the inner diameter of the outlet pipe 15, and the length of the connecting pipe is 1 to 3 times its inner diameter. This structural design significantly shortens the pulsation transmission path, reduces flow resistance, and allows pressure pulsations to be absorbed by the nitrogen tank within the shortest path, achieving optimal pulsation attenuation. Through the above design, the pressure pulsation amplitude of both outlet pipes 15 is controlled at an extremely low level, effectively reducing pipeline vibration and valve erosion, extending system service life, and improving the overall operational safety of the device. Simultaneously, the pressure and flow output of the two pipelines are highly consistent, fully meeting the core requirements of the four-nozzle opposed gasification process for low pulsation, uniform pressure, and stable flow in the feeding system.

[0035] The hydraulic control system is used to control the operating status of the diaphragm pump and ensure the safe and stable operation of the equipment. The hydraulic control system mainly includes a hydraulic oil tank, a diaphragm stroke control system, a lubrication system, a flushing system, an overpressure protection and venting system, oil replenishment and discharge pipelines, and infeed / outfeed instrumentation devices. The diaphragm stroke control system monitors the working position of the diaphragm in real time through a stroke control valve. When the diaphragm displaces beyond its limit due to wear, oil temperature changes, or other reasons, the stroke control system automatically opens the oil replenishment and discharge solenoid valve to add or discharge an appropriate amount of hydraulic oil to the cavity and cylinder 10, causing the diaphragm to return to the set working range. This ensures that the diaphragm always operates within the safe stroke range, avoiding diaphragm damage or equipment failure due to excessive deformation. The lubrication system, through a lubricating oil pump and distribution pipelines, continuously supplies sufficient cooling lubricant to all moving parts of the power end 2 (including the crankshaft 4 and support bearing 6, connecting rod 22 and crankshaft, crosshead 23 and guide plate 26, etc.), reducing friction and wear of the moving parts, lowering heat generation, and extending the service life of the moving components. The flushing system continuously flushes the piston rod 7 and piston body 8 through the flushing oil pump and oil pipeline to lubricate and cool them, thereby ensuring the smooth movement of the piston body 8. The overpressure protection system automatically opens the pressure relief valve to relieve pressure when the system pressure exceeds a set threshold, preventing equipment damage or safety accidents caused by accidental overpressure. The venting system is used to discharge gases contained in the propellant fluid back to the return oil tank through a check valve and return oil pipe after initial equipment startup or maintenance, eliminating accumulated gas in the diaphragm chamber and pipelines, and preventing system pressure fluctuations and cavitation damage to seals and components caused by gas mixing. The oil replenishment and drainage pipelines are used for replenishing and draining oil in the propellant system, ensuring stable operation of the diaphragm pump. The inlet and outlet instrumentation devices include pressure gauges, pressure transmitters, and other monitoring instruments installed on the inlet pipe 13 and outlet pipe 15, used to monitor the inlet and outlet pressures in real time, providing operators with operating status references and providing control signal inputs to the electrical auxiliary control system. The components, their connections, and control principles of the aforementioned hydraulic control system are all well-known technologies in the field. Those skilled in the art can make specific selections and parameter settings according to actual working conditions, and will not elaborate further here.

[0036] The electrical auxiliary control system uses a PLC (Programmable Logic Controller) as its core control unit, responsible for all automated control functions of the diaphragm pump, including start-stop interlocking, speed regulation, status monitoring, fault protection, and remote communication. The system collects real-time operating parameters from various types of sensors (including but not limited to inlet / outlet pressure sensors, flow sensors, temperature sensors, oil pressure sensors, and vibration sensors) installed at key locations on the equipment. The collected analog signals are converted into digital signals and sent to the PLC controller for processing. Based on preset control logic and process parameters, the PLC controller automatically controls the start-stop of the main motor, speed regulation, and the on / off state of various solenoid valves, achieving automatic start-stop and stepless speed regulation of the diaphragm pump to adapt to different slurry conveying requirements. When monitored operating parameters exceed the set safety threshold, the PLC controller promptly issues audible and visual alarm signals and automatically takes corresponding protective measures (such as automatic shutdown, pressure relief, and switching to a backup system) according to the fault level, effectively preventing equipment damage and production accidents. The remote communication function uploads real-time operating status data, alarm information, and historical trend data of the equipment to the DCS system in the central control room via industrial Ethernet or fieldbus, enabling remote centralized monitoring and unified management of the equipment. This allows operators to fully grasp the equipment's operating status from the central control room and promptly detect and handle abnormal situations. The hardware configuration, software programming, control logic, and communication protocols of the aforementioned PLC control system are all technologies well-known in the field. Those skilled in the art can design and implement them specifically according to actual control needs and process requirements, and will not be elaborated further here.

[0037] It is understood that the above specific description of the present invention is only for illustrating the present invention and is not limited to the technical solutions described in the embodiments of the present invention. Those skilled in the art should understand that modifications or equivalent substitutions can still be made to the present invention to achieve the same technical effect; as long as the use needs are met, they are all within the protection scope of the present invention.

Claims

1. A four-cylinder single-acting high-pressure diaphragm pump, comprising a power transmission system (1), a power end (2) connected to and driven by the power transmission system (1), and a hydraulic end (3) connected to the power end (2), characterized in that, The power end (2) includes a crankshaft (4), a housing (5), and a linkage mechanism. The crankshaft (4) is connected to the housing (5) via multiple support bearings (6) and is connected to the power transmission system (1) via a coupling. The crankshaft (4) has a four-crank structure, and each crank is connected to one of the linkage mechanisms. The four linkage mechanisms are respectively connected to the piston rods (7) of four pistons fixed in the edge of the housing (5). The hydraulic end (3) includes four diaphragm chambers (9). Each diaphragm chamber (9) is connected to and communicates with the housing (5) of the power end (2) via a cavity and a cylinder (10). The piston body (8) of the piston can perform reciprocating linear motion, causing the diaphragm in the diaphragm chamber (9) to undergo elastic deformation, so that the diaphragm cavity inside the diaphragm chamber... The volume increases and decreases periodically. The inlet and outlet of each diaphragm chamber (9) are directly connected to a feed valve box (11) and a discharge valve box (12). Two feed valve boxes (11) are connected to a feed pipe (13), and two other feed valve boxes (11) are connected to another feed pipe (13). The two feed pipes (13) are connected to the feed source after passing through a feed compensation device (14). Two discharge valve boxes (12) are connected to a discharge pipe (15), and two other discharge valve boxes (12) are connected to another discharge pipe (15). The two discharge pipes (15) are independent of each other, and a discharge compensation device (16) is provided at the discharge port of each discharge pipe (15). The two discharge compensation devices (16) form a parallel arrangement structure.

2. The four-cylinder single-acting high-pressure diaphragm pump according to claim 1, characterized in that, The four cranks of the crankshaft (4) are, from the direction closest to the coupling of the power transmission system (1) to the direction furthest away, the first crank (17), the second crank (18), the third crank (19), and the fourth crank (20), respectively. Each pair of adjacent cranks is connected by a curved streamlined crank arm (21). The phase angle between the first crank (17) and the second crank (18) is 180°, the phase angle between the third crank (19) and the fourth crank (20) is 180°, and the phase angle between the second crank (18) and the third crank (19) is 90°. The first crank (17) and the second crank (18) share the same working unit of the hydraulic end (3) of the discharge pipe (15), and the third crank (19) and the fourth crank (20) share another working unit of the hydraulic end (3) of the other discharge pipe (15).

3. A four-cylinder single-acting high-pressure diaphragm pump according to claim 1, characterized in that, The linkage mechanism includes a connecting rod (22), a crosshead (23), and a connecting rod (24). The connecting rod (22) is connected to the crank. The crosshead (23) is connected to the end of the connecting rod (22) through a pin bearing (25). The crosshead (23) reciprocates along the inside of the guide plate (26) provided inside the housing (5). The connecting rod (24) is connected to the end of the crosshead (23). The connecting rod (24) is fixedly connected to the piston rod (7) through a clamp (27).

4. A four-cylinder single-acting high-pressure diaphragm pump according to claim 1, characterized in that, The crankshaft (4) is connected to the housing (5) by three support bearings (6), which are respectively located at both ends and the middle of the crankshaft (4).

5. A four-cylinder single-acting high-pressure diaphragm pump according to claim 1, characterized in that, The valves in the feed valve box (11) and the discharge valve box (12) are both cone valves, and the valve box bodies (5) are all made of castings.

6. A four-cylinder single-acting high-pressure diaphragm pump according to claim 1, characterized in that, The discharge compensation device (16) is a nitrogen tank to attenuate the pressure pulsation of the two discharge pipes (15).

7. A four-cylinder single-acting high-pressure diaphragm pump according to claim 6, characterized in that, The nitrogen tank is filled with gas at a pressure of 0.4 to 0.65 times the working pressure.

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