Ultra-high pressure reciprocating double pump set

Abstract

The application discloses a superhigh-pressure reciprocating double-pump pump set, and belongs to the technical field of superhigh-pressure water jet cleaning equipment, which comprises a superhigh-pressure reciprocating pump, a gear transmission box, a power source and a shared lubricating and cooling system, two superhigh-pressure reciprocating pumps are arranged in mirror image, a crankshaft is arranged in the superhigh-pressure reciprocating pump, the gear transmission box is arranged between the two superhigh-pressure reciprocating pumps, the gear transmission box is in transmission connection with the two superhigh-pressure reciprocating pumps through the crankshafts, the power source is in transmission connection with the gear transmission box, and the shared lubricating and cooling system is arranged on the outer side walls of the two superhigh-pressure reciprocating pumps. The application has the advantages of multi-function, greatly reduced equipment procurement cost and maintenance cost, compact structure, greatly saved land occupation area, high operation efficiency, simultaneous completion of high-pressure impact stripping and low-pressure flushing and sewage removal in the same working area, simple and reliable structure, and suitability for harsh working conditions such as high dust, high vibration and moisture of the superhigh-pressure cleaning equipment.

Description

Technical Field

[0001] This invention relates to the field of ultra-high pressure water jet cleaning equipment technology, specifically to an ultra-high pressure reciprocating dual-pump unit. Background Technology

[0002] Ultra-high pressure water jet cleaning technology is widely used in industrial cleaning, rust removal, cutting, deburring and other fields. Existing ultra-high pressure cleaning equipment usually uses a single ultra-high pressure reciprocating pump as a power source. The pump is driven by a motor to pressurize the water to an ultra-high pressure state (usually 1000-3200 bar), and then the water is ejected through the nozzle to form a high-speed water jet for operation.

[0003] In existing technologies, a single ultra-high pressure reciprocating pump is limited by the inherent relationship between plunger diameter and output pressure—the smaller the plunger diameter, the higher the output pressure but the lower the flow rate; the larger the plunger diameter, the higher the output flow rate but the lower the pressure. Therefore, a single device cannot simultaneously meet the operational needs of both high-pressure, low-flow and low-pressure, high-flow conditions. When faced with complex on-site tasks (such as requiring high-pressure impact stripping followed by low-pressure, high-flow flushing and drainage), users often need to purchase two or more ultra-high pressure cleaning devices with different pressure and flow configurations to switch between different processes.

[0004] This existing solution has the following drawbacks: High equipment investment costs: Users need to purchase two or more pieces of equipment, resulting in a large initial investment; Limited work space: When multiple pieces of equipment are on site at the same time, they occupy a lot of space and are difficult to arrange in space-constrained work sites (such as inside a ship's cabin, underground, inside a workshop, etc.). Switching and relocation time: Switching equipment and rewiring between different processes is required, which seriously affects work efficiency and causes significant delays in the project schedule; Low energy efficiency: Each piece of equipment needs to be equipped with an independent motor and drive system, resulting in high overall energy consumption.

[0005] Therefore, how to provide an ultra-high pressure reciprocating dual-pump pump set to overcome the shortcomings of the existing technology is a technical problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0006] To address this, the present invention provides an ultra-high pressure reciprocating dual-pump unit to solve the problems of high cost, large site occupation, and low operating efficiency caused by the inability of a single ultra-high pressure cleaning device to simultaneously meet the requirements of different pressure and flow conditions, requiring users to purchase multiple devices.

[0007] To achieve the above objectives, the present invention provides the following technical solution: This invention discloses an ultra-high pressure reciprocating dual-pump pump set, comprising: Two ultra-high pressure reciprocating pumps are provided in a mirror-arranged manner, and each ultra-high pressure reciprocating pump has a crankshaft inside. A gear transmission box is disposed between the two ultra-high pressure reciprocating pumps, and the gear transmission box is connected to the two ultra-high pressure reciprocating pumps respectively via a crankshaft; A power source is connected to the gear transmission box and is used to provide power to the two ultra-high pressure reciprocating pumps. A shared lubrication and cooling system is installed on the outer wall of the two ultra-high pressure reciprocating pumps, and the shared lubrication and cooling system is used to provide lubrication and cooling for the two ultra-high pressure reciprocating pumps.

[0008] Furthermore, the gearbox includes: The gearbox is mounted on the outer wall of the two ultra-high pressure reciprocating pumps; A drive shaft is rotatably connected to the inside of the gearbox, and the end of the drive shaft extends out of the gearbox and is connected to a power source; The drive gear is mounted on the circumferential sidewall of the drive shaft; There are two driven gears, which are mounted on the crankshaft via splines. The driven gears can slide axially on the crankshaft and can mesh with the driving gears. Two threaded drive clutch assemblies are provided and are located between the driven gear and the gearbox. The threaded drive clutch assemblies are used to control the connection state between the driven gear and the driving gear.

[0009] Furthermore, the threaded drive clutch assembly includes: An externally threaded screw is rotatably connected to the gearbox body, and the externally threaded screw is coaxially arranged with the crankshaft. An internally threaded movable nut is disposed inside the gearbox body and threadedly connected to an externally threaded screw. When the externally threaded screw rotates, the internally threaded movable nut moves axially along the externally threaded screw. A bearing is installed between the internally threaded movable nut and the driven gear. The inner ring of the bearing is fixedly connected to the internally threaded movable nut, and the outer ring of the bearing is fixedly connected to the driven gear. The limiting grooves are arranged in pairs and are formed on the inner side wall of the gearbox body; The limiting pins are arranged in pairs, with one end slidably connected in the limiting groove and the other end connected to the outer wall of the internal thread movable nut. The limiting pins are used to constrain the internal thread movable nut to move axially and not to rotate with the external thread screw.

[0010] Furthermore, the top of the gearbox is provided with an observation window for observing the connection status between the driven gear and the driving gear.

[0011] Furthermore, the two ultra-high pressure reciprocating pumps can be equipped with plungers of different diameters to achieve different pressure-flow output characteristics.

[0012] Furthermore, a hexagonal hole is provided at the end of the externally threaded screw.

[0013] Furthermore, the observation window is detachably mounted on the top of the gearbox body by bolts, and the observation window is made of transparent tempered glass.

[0014] Furthermore, the outer wall of the gearbox is provided with indicator marks for displaying the "engagement" and "disengagement" directions.

[0015] Furthermore, a coupling is installed at the output end of the power source, and the power source is connected to the drive shaft through the coupling.

[0016] Furthermore, the power source is an electric motor or an internal combustion engine.

[0017] The present invention has the following advantages: This invention, by setting up a gear transmission box and two ultra-high pressure reciprocating pumps, and sharing a power source, water inlet system and lubrication and cooling system, eliminates the need for users to purchase multiple devices, significantly reducing equipment procurement and maintenance costs. Furthermore, the overall structure is compact, saving a significant amount of floor space compared to two independent devices, making it convenient for use in space-constrained work sites and reducing site occupancy.

[0018] By setting up a purely mechanical threaded drive clutch assembly, the dual pumps can operate simultaneously or independently. Users can flexibly choose to operate one pump or the two pumps in coordination according to actual working conditions. When only one pump needs to operate, the threaded drive clutch assembly can quickly switch to the single pump operating mode, reducing downtime. The driven gear of the other pump is completely disengaged from the driving wheel, and no power is transmitted to the crankshaft and plunger, avoiding the energy waste caused by the traditional dual pumps having to operate simultaneously. Furthermore, the purely mechanical threaded drive clutch assembly has a simple and reliable structure, eliminating the need for easily damaged parts such as solenoid valves and pneumatic components. It has higher reliability and service life under harsh working conditions such as high dust, high vibration, and humidity in ultra-high pressure cleaning equipment.

[0019] By configuring plungers of different diameters on two ultra-high pressure reciprocating pumps, the same equipment can achieve both "high pressure and low flow" and "low pressure and high flow" output capabilities. It can complete both high-pressure impact stripping and low-pressure flushing and sewage discharge processes in the same working area without switching equipment, meeting the needs of composite processes and achieving high operating efficiency. Furthermore, the pressure and flow parameters of the two pumps can be flexibly adjusted, making it widely applicable and highly expandable. Attached Figure Description

[0020] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0021] The structures, proportions, sizes, etc. illustrated in this specification are only for the purpose of assisting those skilled in the art in understanding and reading the content disclosed herein, and are not intended to limit the conditions under which the present invention can be implemented. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in the proportions, or adjustments to the size, without affecting the effects and objectives that the present invention can produce, should still fall within the scope of the technical content disclosed in the present invention.

[0022] Figure 1 This is an overall structural diagram of the ultra-high pressure reciprocating dual-pump pump unit provided by the present invention; Figure 2 A perspective view of the ultra-high pressure reciprocating dual-pump pump unit provided by the present invention; Figure 3 A structural diagram of the main body of the ultra-high pressure reciprocating dual-pump pump set provided by the present invention; Figure 4 A cross-sectional view of the ultra-high pressure reciprocating dual-pump pump unit provided by the present invention; Figure 5 Provided by the present invention Figure 4 Enlarged view of the A-structure; Figure 6 This is a cross-sectional view of the ultra-high pressure reciprocating dual-pump pump set provided by the present invention. Figure 7 Provided by the present invention Figure 6 Enlarged view of the B-structure.

[0023] In the diagram: 1 Power source; 2 Gear transmission box; 21 Driving gear; 22 Driven gear; 23 External threaded screw; 231 Hexagonal hole; 24 Internal threaded sliding nut; 25 Bearing; 26 Limit pin; 27 Limit groove; 28 Gearbox body; 29 Drive shaft; 3 Ultra-high pressure reciprocating pump; 31 Crankshaft; 4 Shared lubrication and cooling system; 5 Observation window. Detailed Implementation

[0024] The following specific embodiments illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0025] Please refer to Figures 1-7 The ultra-high pressure reciprocating dual-pump pump set disclosed in this invention will now be described. This invention consists of four parts, as follows: Figure 1 , Figure 2 , Figure 3 As shown, the system includes an ultra-high pressure reciprocating pump 3, a gear transmission box 2, a power source 1, and a shared lubrication and cooling system 4. Two ultra-high pressure reciprocating pumps 3 are arranged in a mirror image. A crankshaft 31 is installed inside each ultra-high pressure reciprocating pump 3. The gear transmission box 2 is located between the two ultra-high pressure reciprocating pumps 3 and is connected to the two ultra-high pressure reciprocating pumps 3 via the crankshaft 31. The power source 1 is connected to the gear transmission box 2 and is used to provide power to the two ultra-high pressure reciprocating pumps 3. The shared lubrication and cooling system 4 is located on the outer wall of the two ultra-high pressure reciprocating pumps 3 and is used to provide lubrication and cooling to the two ultra-high pressure reciprocating pumps 3.

[0026] The two ultra-high pressure reciprocating pumps 3 of this application are respectively installed on both sides of the gear transmission box 2 and arranged in a mirror symmetrical manner. Each pump body is equipped with a plunger, and the diameter of the plunger in the two ultra-high pressure reciprocating pumps 3 can be the same or different. The gear transmission box 2 has a built-in gear transmission mechanism and a purely mechanical threaded drive clutch assembly, which splits the power output from the power source 1 to the two ultra-high pressure reciprocating pumps 3.

[0027] The two ultra-high pressure reciprocating pumps 3 also include some shared systems, such as a shared inlet water system, an integrated output pipeline, and a shared lubrication and cooling system 4. The shared inlet water system is used to supply water to the two ultra-high pressure reciprocating pumps 3; the integrated output pipeline is used to collect or separately lead the high-pressure outlets of the two pumps to the working area. The above three systems are the basic structure of the ultra-high pressure reciprocating pumps 3, which are known to those skilled in the art, and only need to be adapted according to the setting of the two ultra-high pressure reciprocating pumps 3.

[0028] Preferably, the power source 1 is an electric motor or an internal combustion engine. This application uses an electric motor or internal combustion engine as the sole power source 1, and outputs power to two ultra-high pressure reciprocating pumps 3 through a drive shaft 29.

[0029] Preferably, a coupling is installed at the output end of the power source 1, and the power source 1 is connected to the drive shaft 29 through the coupling.

[0030] In one possible embodiment, the shared lubrication and cooling system 4 includes a crosshead 1, a crosshead 2, an oil suction pump, and an oil cooling heat exchanger. An oil passage hole 1 is provided on the inner wall between the two ultra-high pressure reciprocating pumps 3 and the gearbox 28, and an oil passage hole 2 is provided on the inner wall of the gearbox 28. The two ultra-high pressure reciprocating pumps 3 are internally connected to the gear transmission box 2 through the oil passage hole 1 and the oil passage hole 2, so that the cooling oil can circulate between the two ultra-high pressure reciprocating pumps 3. The oil suction pump is installed on the outer wall of the two ultra-high pressure reciprocating pumps 3. Each side of the oil suction pump is connected to an oil suction pipe, and each oil suction pipe extends into the chamber of one ultra-high pressure reciprocating pump 3. The oil cooling heat exchanger is installed above the oil suction pump and is connected to the oil suction pump through a pipe. Each side of the oil cooling heat exchanger is connected to an oil injection pipe. The two oil injection pipes are used to inject oil into the crankshaft 31 inside the two ultra-high pressure reciprocating pumps 3. Crosshead 1 and crosshead 2 are connected to the oil cooling heat exchanger through pipes. Crosshead 1 and crosshead 2 are respectively installed on the inner and outer walls of the two ultra-high pressure reciprocating pumps 3. Crosshead 1 and crosshead 2 are used for oil pouring.

[0031] This application integrates two ultra-high pressure reciprocating pumps 3 into one device, sharing a power source 1, water inlet system, and lubrication and cooling system. This not only results in a compact structure and reduced space occupancy but also optimizes costs. By incorporating a purely mechanical threaded drive clutch assembly, the two pumps can operate simultaneously or independently, allowing users to flexibly choose between single-pump operation or dual-pump coordinated operation based on actual working conditions. The mechanical clutch structure is simple and reliable, requiring no additional electromagnetic or pneumatic control energy, thus reducing system complexity and failure rate.

[0032] Preferably, the two ultra-high pressure reciprocating pumps 3 can be equipped with plungers of different diameters to achieve different pressure-flow output characteristics. The two pumps can be equipped with plungers of different diameters, such as 19.05mm, 20.64mm, 26mm, and 28mm. By configuring the two ultra-high pressure reciprocating pumps 3 with plungers of different diameters, the same equipment can achieve both "high pressure, low flow" and "low pressure, high flow" output capabilities, meeting the requirements of complex processes.

[0033] like Figure 3 , Figure 4 , Figure 5As shown, the gear transmission box 2 includes a gearbox body 28, a drive shaft 29, a driving gear 21, a driven gear 22, and a threaded drive clutch assembly. The gearbox body 28 is mounted on the outer wall of the two ultra-high pressure reciprocating pumps 3. The drive shaft 29 is rotatably connected to the inside of the gearbox body 28, with its end extending out of the gearbox body 28 and connected to the power source 1. The driving gear 21 is mounted on the circumferential side wall of the drive shaft 29 and rotates synchronously with the drive shaft 29, serving as the power input end. Two driven gears 22 are provided and mounted on the crankshaft 31 via splines. The driven gears 22 can slide axially on the crankshaft 31 and transmit rotational power to the crankshaft 31 through spline engagement. The crankshaft 31 is connected to a plunger, driving the pumps. The driven gears 22 can mesh with the driving gears 21. Two threaded drive clutch assemblies are provided and located between the driven gears 22 and the gearbox body 28. The threaded drive clutch assembly is used to control the connection state between the driven gears 22 and the driving gears 21.

[0034] like Figure 4 — Figure 7 As shown, the gear transmission box 2 is equipped with two threaded drive clutch assemblies, which respectively control the power engagement and disengagement of the two ultra-high pressure reciprocating pumps 3. Taking the threaded drive clutch assembly of one pump as an example (the other is exactly the same), the threaded drive clutch assembly includes an external threaded screw 23, an internal threaded moving nut 24, a bearing 25, a limiting groove 27, and a limiting pin 26. The external threaded screw 23 is rotatably connected in the gearbox 28 and is coaxially arranged with the crankshaft 31. Its external thread engages with the internal threaded moving nut 24. The operator rotates the external threaded screw 23 using a tool. An internally threaded movable nut 24 is disposed inside the gearbox body 28 and is threadedly connected to an externally threaded screw 23. The internally threaded movable nut 24 and the externally threaded screw 23 are threadedly engaged. When the externally threaded screw 23 rotates, the internally threaded movable nut 24 moves axially along the externally threaded screw 23. A bearing 25 is installed between the internally threaded movable nut 24 and the driven gear 22. The internally threaded movable nut 24 and the driven gear are connected by the bearing 25. The inner ring of the bearing 25 is fixedly connected to the internally threaded movable nut 24, and the outer ring of the bearing 25 is fixedly connected to the driven gear 22. The function of the bearing 25 is to enable the internally threaded movable nut 24 to drive the driven gear 22 to move back and forth axially. At the same time, when the driven gear 22 rotates, the bearing 25 isolates the rotational motion, keeping the internally threaded movable nut 24 stationary and not rotating with the driven gear 22. The limiting grooves 27 are arranged in pairs and are formed on the inner side wall of the gearbox body 28. The internal thread moving nut 24 is provided with a limiting pin 26 between it and the gearbox body 28. The limiting pins 26 are arranged in pairs, with one end slidably connected in the limiting groove 27 and the other end connected to the outer side wall of the internal thread moving nut 24. The limiting pins 26 are used to constrain the internal thread moving nut 24 to move axially and not to rotate with the external thread screw 23.

[0035] Operating principle of threaded drive clutch assembly: Engagement state: When the operator rotates the external threaded screw 23 in the forward direction, the internal threaded moving nut 24 moves forward along the axial direction of the external threaded screw 23, and pushes the driven gear 22 to slide forward along the spline on the crankshaft 31 through the bearing 25 until the driven gear 22 and the driving gear 21 are fully engaged. At this time, the power is transmitted to the pump from the driving gear 21 → driven gear 22 → spline → crankshaft 31, and the pump starts to work.

[0036] Separation state: When the operator rotates the external thread screw 23 in the opposite direction, the internal thread moving nut 24 moves backward along the axis of the external thread screw 23. Through the bearing 25, it pulls the driven gear 22 to slide backward along the spline on the crankshaft 31, causing the driven gear 22 to disengage from the driving gear 21. At this time, the power transmission is interrupted and the pump stops working.

[0037] It is worth noting that after the "engagement" or "disengagement" operation is completed, if not locked, the external threaded screw 23 may rotate on its own due to the rotation of the crankshaft 31, the rotation of the driven gear, and the overall vibration of the equipment. Although a bearing is provided between the rotating component and the external threaded screw 23, the friction of the bearing is still sufficient to generate a rotational tendency, which may lead to an unexpected change in the meshing state of the driving gear 21 and the driven gear 22, and in severe cases, may cause a "tooth breakage" accident, damaging the gear tooth surface. Therefore, a rocker arm self-locking assembly is added to the gear transmission box 2 to mechanically lock the external threaded screw 23 and restrict its rotational freedom. This device borrows from the existing mature indexing pin structure (not the technical solution of this patent), and those skilled in the art only need to make adaptive adjustments according to this application.

[0038] The rocker arm self-locking device includes a rocker arm, an indexing pin, and pin holes. The rocker arm is mounted on the end of the external threaded screw 23. One end of the rocker arm is fixedly connected to the external threaded screw 23 and can rotate synchronously with the external threaded screw 23. The other end of the rocker arm is equipped with an indexing pin. Several pin holes are formed on the outer wall of the gearbox 28. The pin holes are used to engage with the indexing pin to fix the external threaded screw 23. The pin holes are evenly distributed along the pitch circle centered on the axis of the external threaded screw 23. The number and distribution angle of the pin holes determine the minimum adjustment step of the screw locking position.

[0039] The indexing pin has two working states: retracted and extended. Retracted state: Pull up and rotate the indexing pin (e.g., rotate 90°) to retract the pin into the pin body, with the end of the pin not protruding from the lower end face of the rocker arm. Extended state: Pull up and rotate the pin again (rotate 90°), and the end of the pin protrudes from the lower end face of the rocker arm and can be inserted into the pin hole.

[0040] When unlocking, the operator pulls and rotates the indexing pin to retract it into the pin body, switching to the "retracted state". At this time, the end of the pin no longer protrudes from the lower end face of the rocker arm and will not interfere with the pin hole. The operator rotates the external thread screw 23, and the rocker arm rotates with the external thread screw 23. The indexing pin is in the retracted state and can freely pass through each pin hole without obstruction.

[0041] When locking, the operator slightly rotates the external threaded screw 23 (within the permissible fine-tuning range) to align the indexing pin at the end of the rocker arm with the nearest pin hole (a hole on the equal-angle pitch circle); the operator then pulls up the indexing pin again and rotates it in the opposite direction to switch to the "pop-out state," at which point the end of the pin extends out of the lower end face of the rocker arm and automatically inserts into the aligned pin hole. At this time, the external threaded screw 23 forms a rigid connection with the gearbox 28 through the rocker arm, and the rotational freedom of the external threaded screw 23 is completely restricted. Even if the crankshaft 31 rotates and the driven gear 22 rotates during equipment operation, causing vibration, the indexing pin remains in the pin hole, ensuring reliable locking.

[0042] The indexing pin is an existing mature technology and is not part of the innovation of this application. The innovation of this application lies in: applying the indexing pin structure to the external threaded screw 23 of the threaded drive clutch assembly of an ultra-high pressure reciprocating dual pump set for locking, and combining it with the rocker arm and pin hole to form a complete safety locking solution.

[0043] like Figure 1 , Figure 3 As shown, the top of the gearbox 28 is provided with an observation window 5 for observing the connection state between the driven gear 22 and the driving gear 21. Preferably, the observation window 5 is detachably mounted on the top of the gearbox 28 by bolts, and the observation window 5 is made of transparent tempered glass.

[0044] It is worth noting that in actual operation, when the operator drives the driven gear 22 to mesh with the driving gear 21 by rotating the external threaded screw 23, if the teeth of the driving gear 21 and the driven gear 22 are not aligned (i.e., tooth tip to tooth tip), the driven gear 22 cannot smoothly slide into the meshing position. Forcibly rotating the external threaded screw 23 may cause damage to the tooth surface or failure of meshing. This application solves this problem by setting an observation window 5 and further provides a method for tooth alignment.

[0045] 1. Settings for Observation Window 5 An observation window 5 is provided on the top of the gearbox 28 at the meshing position of the driving gear 21 and the driven gear 22. The size of the observation window 5 should be sufficient for the operator to clearly observe the relative positions of the teeth of the driving gear 21 and the driven gear 22. The observation window 5 is made of a transparent material (such as tempered glass or plexiglass), which facilitates observation and prevents external impurities from entering the gearbox 2. Preferably, the observation window 5 is detachably installed by bolts, making it easy to open for maintenance.

[0046] The observation window 5 is preferably positioned so that the operator can simultaneously see the meshing teeth of the driving gear 21 and the driven gear 22 while standing. Preferably, it is located on the top or side of the gearbox 28 corresponding to the meshing area.

[0047] 2. Single pump gear operation procedure Taking the engagement of the threaded drive clutch assembly of one of the ultra-high pressure reciprocating pumps 3 as an example, the gear operation is performed according to the following steps: S1. Preparation: Ensure the system is in a stopped state, the motor is powered off, and confirm safety. S2, Manually drive the drive gear 21: The operator uses the drive shaft 29 to put the drive gear 21 into a manually rotatable state; S3. Preliminary observation: Observe the relative position of the driving gear 21 and the driven gear 22 through the observation window 5 to determine whether the teeth of the two gears are in a meshing state (i.e., tooth groove to tooth tip). S4. Gear Alignment: If the tips of the two gear teeth are facing each other (cannot mesh), the operator slowly rotates the driving gear 21 through the drive shaft 29 while continuously observing the relative position changes of the teeth through the observation window 5. When it is observed that the tooth groove of the driving gear 21 is completely aligned with the tooth tip of the driven gear 22 (or the tooth tip of the driving gear 21 is aligned with the tooth groove of the driven gear 22), stop rotating the driving gear 21. At this time, the two gears are in a position where they can mesh smoothly. S5. Complete engagement: Keep the driving gear 21 in the same position, and the operator rotates the external thread screw 23 in the forward direction, so that the internal thread moving nut 24 drives the driven gear 22 to move axially along the crankshaft 31, so that the driven gear 22 smoothly slides into the engagement position with the driving gear 21, and completes the engagement. S6. Start-up: After confirming that the engagement is complete, start the power source 1. The power is transmitted to the crankshaft 31 through the driving gear 21, the driven gear 22, and the spline, and the pump starts to work.

[0048] 3. Dual-pump simultaneous gear operation procedure When two pumps need to be engaged simultaneously, the operator must perform the gear engagement and meshing operations for each pump separately. The specific steps are as follows: A1. Observe the relative positions of the teeth of the driving gear 21 and the two driven gears 22 through the observation window 5; A2. If both driven gears 22 need to be aligned, the operator rotates the drive gear 21 to first align the teeth of the drive gear 21 with one of the driven gears 22, and then rotates the corresponding external thread screw 23 to complete the pump engagement. A3. Keep the position of the drive gear 21 unchanged (or rotate it again as needed), and observe through the observation window 5 whether the teeth of the other driven gear 22 are aligned with those of the drive gear 21. Since the initial phases of the two driven gears 22 on the crankshaft 31 may be different, they may need to be adjusted individually. A4. If the teeth of the driven gear 22 and the driving gear 21 are not aligned during the second adjustment, the operator can rotate the driving gear 21 again to align it with the teeth of the driven gear 22 (at this time, the pump that was engaged in the first engagement has been engaged, and the driving gear 21 needs to overcome the resistance of the pump that was engaged in the first engagement, but the pump that was engaged in the first engagement is in an unloaded state and can still withstand the force), and then rotate the external thread screw 23 to complete the engagement. A5. After both threaded drive clutch components are engaged, start power source 1, and both pumps will run simultaneously.

[0049] like Figure 3 As shown, the end of the externally threaded screw 23 has a hexagonal hole 231. The end of the externally threaded screw 23 can be provided with a hexagonal hole 231 or a hexagonal head to facilitate operation by the operator using tools.

[0050] Preferably, the outer wall of the gearbox 28 is provided with indicator marks for displaying the "engagement" and "disengagement" directions.

[0051] The ultra-high pressure reciprocating dual-pump pump set of this application has the following operating modes: Single-pump operation mode: Only the threaded drive clutch assembly of one of the ultra-high pressure reciprocating pumps 3 is engaged, while the threaded drive clutch assembly of the other pump remains disengaged, enabling independent operation of a single pump. Suitable for applications requiring only one pressure and flow parameter.

[0052] Dual-pump simultaneous operation mode: The threaded drive clutch assemblies of two ultra-high pressure reciprocating pumps 3 are engaged simultaneously, and both pumps operate at the same time. Suitable for working conditions requiring large flow rates or the coordinated operation of two different pressure and flow rates.

[0053] Sequential switching mode: According to process requirements, first engage the threaded drive clutch assembly of one of the ultra-high pressure reciprocating pumps 3 to complete the high pressure impact operation, then disengage the threaded drive clutch assembly of that pump, engage the threaded drive clutch assembly of another pump, and switch to that pump for low pressure flushing operation. The entire process only requires stopping the machine to operate the threaded drive clutch assembly.

[0054] As a second embodiment of this application, dual-pump collaborative operation—high-pressure stripping + low-pressure flushing—can be achieved by selecting plungers of different diameters: one ultra-high pressure reciprocating pump 3 is equipped with a 28mm plunger, with a rated output pressure of 1500 bar and a flow rate of 89.7 liters / minute; the other ultra-high pressure reciprocating pump 3 is equipped with a 19.05mm plunger, with a rated output pressure of 2800 bar and a flow rate of 48.9 liters / minute.

[0055] During operation, the operator engages both threaded drive clutch assemblies and selects "dual-pump mode," with both pumps running simultaneously. One ultra-high pressure reciprocating pump 3 outputs a high-pressure, low-flow water jet to strike and peel away stubborn dirt or rust from the workpiece surface; the other ultra-high pressure reciprocating pump 3 outputs a low-pressure, high-flow water jet to rinse away the peeled dirt from the work area. The outputs of the two pumps converge in the same work area through an integrated pipeline, enabling continuous "striking and rinsing" operation, significantly improving cleaning efficiency.

[0056] As a third embodiment of this application, the dual-pump sequential switching operation is achieved by selecting plungers of the same diameter: two ultra-high pressure reciprocating pumps 3 are configured with plungers of the same diameter, as one in use and one in standby configuration.

[0057] During operation, the operator first engages one of the threaded drive clutch components, and the corresponding pump starts operating. When the pump requires maintenance or malfunctions, the operator reverses the external threaded screw 23 to disengage the threaded drive clutch component, while simultaneously rotating the other external threaded screw 23 in the forward direction to engage the corresponding threaded drive clutch component, achieving non-stop switching and ensuring continuous production.

[0058] Although the present invention has been described in detail above with general descriptions and specific embodiments, modifications or improvements can be made to it, which will be obvious to those skilled in the art. Therefore, all such modifications or improvements made without departing from the spirit of the present invention fall within the scope of protection claimed by the present invention.

Claims

1. A superhigh pressure reciprocating double pump unit, characterized by, include: Two ultra-high pressure reciprocating pumps (3) are provided and arranged in a mirror image. A crankshaft (31) is provided inside the ultra-high pressure reciprocating pump (3). A gear transmission box (2) is set between the two ultra-high pressure reciprocating pumps (3), and the gear transmission box (2) is connected to the two ultra-high pressure reciprocating pumps (3) respectively through a crankshaft (31); The power source (1) is connected to the gear transmission box (2) and is used to provide power to the two ultra-high pressure reciprocating pumps (3); A shared lubrication and cooling system (4) is provided on the outer side wall of the two ultra-high pressure reciprocating pumps (3). The shared lubrication and cooling system (4) is used to provide lubrication and cooling for the two ultra-high pressure reciprocating pumps (3).

2. The super-high pressure reciprocating double pump unit according to claim 1, wherein The gearbox (2) includes: The gearbox (28) is mounted on the outer side wall of the two ultra-high pressure reciprocating pumps (3); The drive shaft (29) is rotatably connected to the inside of the gearbox (28), and the end of the drive shaft (29) extends out of the gearbox (28) and is connected to the power source (1); The drive gear (21) is mounted on the circumferential sidewall of the drive shaft (29); Two driven gears (22) are provided and are mounted on the crankshaft (31) by splines. The driven gears (22) can slide axially on the crankshaft (31) and can mesh with the driving gear (21). Two threaded drive clutch assemblies are provided, which are located between the driven gear (22) and the gearbox (28). The threaded drive clutch assemblies are used to control the connection state between the driven gear (22) and the driving gear (21).

3. The super-high pressure reciprocating double pump unit according to claim 2, wherein The threaded drive clutch assembly includes: An external threaded screw (23) is rotatably connected inside the gearbox (28), and the external threaded screw (23) is coaxially arranged with the crankshaft (31); An internal thread movable nut (24) is disposed inside the gearbox body (28) and threadedly connected to the external thread screw (23). When the external thread screw (23) rotates, the internal thread movable nut (24) moves along the axial direction of the external thread screw (23). A bearing (25) is installed between the internal thread moving nut (24) and the driven gear (22). The inner ring of the bearing (25) is fixedly connected to the internal thread moving nut (24), and the outer ring of the bearing (25) is fixedly connected to the driven gear (22). Limiting grooves (27) are provided in pairs and are formed on the inner side wall of the gearbox body (28); The limiting pins (26) are set in pairs, with one end slidably connected in the limiting groove (27) and the other end of the limiting pins (26) connected to the outer wall of the internal thread moving nut (24). The limiting pins (26) are used to constrain the internal thread moving nut (24) to move axially and not to rotate with the external thread screw (23).

4. The ultra-high pressure reciprocating dual-pump pump set as described in claim 2, characterized in that, The top of the gearbox (28) is provided with an observation window (5) for observing the connection status between the driven gear (22) and the driving gear (21).

5. The ultra-high pressure reciprocating dual-pump pump set as described in claim 1, characterized in that, The two ultra-high pressure reciprocating pumps (3) can be equipped with plungers of different diameters to achieve different pressure-flow output characteristics.

6. The ultra-high pressure reciprocating dual-pump pump set as described in claim 3, characterized in that, The end of the external threaded screw (23) is provided with a hexagonal hole (231).

7. The ultra-high pressure reciprocating dual-pump pump set as described in claim 4, characterized in that, The observation window (5) is detachably mounted on the top of the gearbox body (28) by bolts, and the observation window (5) is made of transparent tempered glass.

8. The ultra-high pressure reciprocating dual-pump pump set as described in claim 6, characterized in that, The outer wall of the gearbox (28) is provided with indicator marks for displaying the "engagement" and "disengagement" directions.

9. The ultra-high pressure reciprocating dual-pump pump set as described in claim 2, characterized in that, The output end of the power source (1) is equipped with a coupling, and the power source (1) is connected to the drive shaft (29) through the coupling.

10. The ultra-high pressure reciprocating dual-pump pump set as described in claim 1, characterized in that, The power source (1) is an electric motor or an internal combustion engine.

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