Ultrahigh-pressure booster pump for low-temperature liquid working medium

Abstract

The utility model relates to an ultrahigh-pressure booster pump for a low-temperature liquid working medium, which comprises a heat-insulating cylinder, a built-in low-temperature liquid, two split type independent plunger pumps, two electromagnetic directional valves, a pressure sensor, a pressure sensor, a pressure sensor, a pressure sensor and a pressure sensor, each electromagnetic reversing valve independently controls the on-off of the input end and the output end of an oil cavity of the corresponding plunger pump, pressurization and return stroke actions are achieved by alternately switching oil ways, the pressurization stages of the two plunger pumps can be alternately or partially overlapped, and continuous output of an ultrahigh-pressure working medium is ensured; pressurizing cavities of the two plunger pumps are immersed in low-temperature liquid of the heat preservation barrel, gasification of a working medium is effectively restrained, the stability of ultrahigh pressure output is ensured, the two electromagnetic reversing valves are used for independently controlling connection and disconnection of oil cavities of the corresponding plunger pumps, and through an alternate or partially-overlapped pressurizing stage mode, high-pressure output is achieved. Output interruption caused by return stroke of a traditional single-pump system is eliminated, and seamless continuous supply of working media is achieved.

Description

Technical Field

[0001] This utility model relates to the field of booster pump technology, specifically to an ultra-high pressure booster pump for cryogenic liquid working fluid. Background Technology

[0002] Waterjet cutting, also known as high-pressure water jet cutting, is a technology that uses high-speed water jets or high-pressure water jets with added abrasives to cut materials. It is widely used for cutting various materials such as metals, stone, glass, and composite materials. Traditional waterjet cutting typically relies on plunger-type reciprocating pumps to achieve continuous ultra-high pressure output. For cutting certain flammable and explosive materials, cryogenic liquid working fluids are required to prevent localized high temperatures during cutting. Traditional waterjet booster pumps are designed for water and are not suitable for directly handling cryogenic liquids such as liquid nitrogen or liquid carbon dioxide. These cryogenic working fluids easily vaporize at room temperature, leading to unstable pressure and making it difficult to achieve continuous ultra-high pressure output. Furthermore, existing cryogenic liquid booster pumps are not designed for high-speed jet cutting and cannot achieve ultra-high pressure conditions of several hundred megapascals.

[0003] The use of cryogenic liquids presents new technical challenges, particularly in preventing pressure fluctuations caused by vaporization of the working fluid during pressurization, and ensuring the continuity and stability of ultra-high pressure working fluid output. Existing booster pumps capable of reaching ultra-high pressure are unsuitable for cryogenic liquids, as vaporization of the working fluid in the pressurization chamber prevents the output of ultra-high pressure working fluid. Furthermore, conventional cryogenic liquid booster pumps, due to their structural limitations, cannot output a continuous and stable ultra-high pressure cryogenic fluid. Utility Model Content

[0004] To address the shortcomings of existing technologies, this utility model provides an ultra-high pressure booster pump for cryogenic liquid working fluids, aiming to solve the problem that existing booster pumps capable of reaching ultra-high pressure are not suitable for cryogenic liquids, and the working fluid cannot output ultra-high pressure working fluid due to vaporization in the booster chamber.

[0005] To achieve the above objectives, this utility model adopts the following technical solution: an ultra-high pressure booster pump for a cryogenic liquid working fluid, comprising: an insulated cylinder containing a cryogenic liquid; two separate independent plunger pumps, the booster chambers of which are completely immersed in the cryogenic liquid within the insulated cylinder; and two electromagnetic reversing valves, each connected to one of the two plunger pumps. Each electromagnetic reversing valve independently controls the on / off state of the input and output ends of the oil chamber of the corresponding plunger pump. The boosting and return actions are achieved by alternately switching the oil circuit. The boosting phases of the two plunger pumps can be selected to alternate or partially overlap to ensure continuous output of the ultra-high pressure working fluid.

[0006] Furthermore, it also includes a displacement sensor and a controller. The displacement sensor is set on the piston rod stroke path of the plunger pump to detect the position of the piston rod in real time. The controller is connected to the displacement sensor and the solenoid directional valve. The control logic of the two solenoid directional valves is implemented in the following way: when the displacement sensor detects that the piston rod of a plunger pump is at the end of the pressurization stage or the return stage, the controller sends a switching signal to the corresponding solenoid directional valve to start the pressurization action of the other plunger pump.

[0007] Furthermore, it also includes an energy storage buffer, which is located inside the insulation cylinder and immersed in a cryogenic liquid. Its input end is connected to the output end of the booster chamber of the two plunger pumps to balance the output pressure fluctuations.

[0008] Furthermore, the cryogenic liquid is either liquid nitrogen or liquid carbon dioxide, and it is the same cryogenic liquid as the pressurizing working fluid.

[0009] Furthermore, the cross-sectional area of ​​the piston rod in the plunger pump that contacts the oil is larger than the cross-sectional area that contacts the working fluid, in order to achieve a hydraulic amplification effect.

[0010] Furthermore, the insulation cylinder is equipped with a thermometer and a level gauge for real-time monitoring of the temperature and level of the cryogenic liquid.

[0011] Furthermore, the booster chamber of the plunger pump is connected to the energy storage buffer via a one-way valve to ensure unidirectional flow of the working fluid.

[0012] Furthermore, the insulation cylinder includes a cylinder body, which has a top-opening structure. A support flange is fixedly installed on the top of the cylinder body, and the support flange is sealed to the insulation cylinder body. All plunger pumps are vertically installed on the top of the insulation cylinder body through the support flange. The support flange has through holes corresponding to the plunger pumps, and the pressurization chamber of the plunger pump enters the insulation cylinder body through the through holes.

[0013] Furthermore, the insulation cylinder is equipped with a cooling liquid inlet and an outlet for injecting cryogenic liquid and discharging vaporized chemical substances.

[0014] Furthermore, the pressurization chamber of the plunger pump draws in the pressurizing working fluid directly from the insulated cylinder.

[0015] The ultra-high pressure booster pump for cryogenic liquid working fluid described in this utility model has the following advantages: by completely immersing the booster chambers of two separate independent plunger pumps in the cryogenic liquid of the insulation cylinder, the vaporization of the working fluid is effectively suppressed, ensuring the stability of the ultra-high pressure output. By using two electromagnetic reversing valves to independently control the on / off of the oil chambers of the corresponding plunger pumps, and through alternating or partially overlapping booster phase modes, the output interruption caused by the return stroke in traditional single-pump systems is completely eliminated, achieving seamless and continuous supply of the working fluid. Attached Figure Description

[0016] Figure 1This is a schematic diagram of an embodiment of the present utility model.

[0017] Explanation of reference numerals in the attached drawings: 1. Insulation cylinder; 11. Support flange; 2. Plunger pump; 21. Solenoid directional valve; 3. Plunger pump; 31. Solenoid directional valve; 4. Piston rod; Detailed Implementation

[0018] Typical embodiments embodying the features and advantages of this utility model will be described in detail in the following description. It should be understood that this utility model can have various variations in different embodiments, all of which do not depart from the scope of this utility model, and the descriptions and illustrations therein are for illustrative purposes only and not intended to limit this utility model.

[0019] In the description of this application, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicating orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0020] To further illustrate the principle and structure of this utility model, the preferred embodiments of this utility model will now be described in detail with reference to the accompanying drawings.

[0021] This utility model relates to the field of booster pump technology, specifically providing an ultra-high pressure booster pump for cryogenic liquid working fluids, which is particularly suitable for continuous ultra-high pressure output scenarios for cryogenic working fluids such as liquid nitrogen and liquid carbon dioxide.

[0022] like Figure 1As shown, an ultra-high pressure booster pump for cryogenic liquid working fluid includes an insulated cylinder 1, two separate independent plunger pumps 2 and 3, and two electromagnetic directional valves 21 and 31. The insulated cylinder 1 is filled with a cryogenic liquid (such as liquid nitrogen or liquid carbon dioxide), and its internal temperature is monitored in real time by a level gauge and a thermometer to ensure a stable cryogenic environment. The booster chambers of the two separate plunger pumps 2 and 3 are completely immersed in the cryogenic liquid in the insulated cylinder 1. Cryogenic immersion inhibits the vaporization of the working fluid, thereby ensuring that the working fluid in the booster chamber remains in a liquid state, avoiding the problem of increased compressibility due to vaporization, and achieving an ultra-high pressure output of hundreds of megapascals.

[0023] Each plunger pump's oil chamber is connected to a corresponding solenoid directional valve. Solenoid valves 21 and 31 independently control the on / off state of the input and output ends of their respective plunger pump oil chambers, driving the pressurization and return strokes of plunger pumps 2 and 3 by alternately switching the oil circuits. Specifically, when the piston rod 4 of a plunger pump is in the pressurization phase, its corresponding solenoid directional valve switches to the high-pressure oil circuit, pushing the piston to compress the working fluid; during the return stroke, the solenoid directional valve switches to the low-pressure oil circuit, causing the piston to reset and draw in new working fluid. The pressurization phases of the two plunger pumps can be alternated or partially overlapped as needed.

[0024] Alternating operation mode: After one plunger pump completes pressurization, the other pump immediately starts pressurization, and the output gap is eliminated through strict timing control;

[0025] Partial overlap mode: The pressurization phases of the two plunger pumps partially overlap in time, ensuring that at least one pump is in pressurization mode at any given time, thereby further smoothing pressure fluctuations and improving output continuity.

[0026] The insulation cylinder 1 is provided with a cooling liquid inlet and a discharge outlet. Before the plunger pumps 2 and 3 are started, a low-temperature liquid is injected into the insulation cylinder 1 through the cooling liquid inlet. After the liquid absorbs heat and vaporizes, it can be discharged through the discharge outlet. When the liquid level meets the requirements, the plunger pumps 2 and 3 can be started. In this utility model, the cooling liquid and the compression working fluid are the same low-temperature liquid. The compression chamber can directly draw the working fluid from the insulation cylinder 1, thereby simplifying the equipment.

[0027] This invention effectively suppresses working fluid vaporization and ensures stable ultra-high pressure output by completely immersing the pressurization chambers of two separate, independent plunger pumps 2 and 3 in a cryogenic liquid within an insulated cylinder. Two electromagnetic reversing valves independently control the on / off state of the corresponding plunger pump's oil chamber, and through alternating or partially overlapping pressurization phases, it completely eliminates output interruptions caused by the return stroke in traditional single-pump systems, achieving seamless and continuous working fluid supply. The separate design simplifies the structure and supports independent maintenance, reducing operating costs. Furthermore, the cryogenic liquid and working fluid share the same origin, further simplifying system integration and eliminating the need for additional cooling devices. This solution systematically solves the problems of vaporization, pressure fluctuation, and continuity of cryogenic working fluids in ultra-high pressure output through cryogenic environment control, dual-pump collaboration, and flexible mode switching, significantly improving the supply efficiency and reliability of high-pressure fluids in industrial scenarios such as high-speed jet cutting.

[0028] Furthermore, it also includes an energy storage buffer, located inside the insulated cylinder 1 and completely submerged in the cryogenic liquid. Its input end is connected to the output end of the booster chambers of the two plunger pumps. This buffer absorbs pressure fluctuations during the working fluid output process and suppresses vaporization through continuous cooling by the cryogenic liquid, further balancing the stability of the output. This design, through the combined effects of cryogenic immersion, dual-pump synergy, and energy storage buffer, solves the problems of vaporization, continuity, and pressure fluctuations of the cryogenic working fluid in ultra-high pressure output, ensuring the stability and consistency of the high-pressure fluid and significantly improving the system's reliability under ultra-high pressure conditions.

[0029] Furthermore, a check valve is installed between the booster chamber of the plunger pump and the accumulator buffer, on the connecting pipeline between the output end of the booster chamber and the input end of the accumulator buffer. This check valve allows the working fluid to flow unidirectionally from the booster chamber to the accumulator buffer, completely blocking reverse flow during the return phase or pressure fluctuations. This design not only avoids energy loss caused by backflow of the working fluid but also ensures that the booster chamber can quickly draw in new working fluid during the return phase, maintaining a continuous pressurization rhythm. Combined with cryogenic immersion and alternating dual-pump control, the introduction of the check valve further optimizes the system's pressure stability and output efficiency, making it suitable for industrial applications with extremely high requirements for the continuity and stability of high-pressure fluids.

[0030] At runtime, Figure 1Taking the following state as an example, at this time, the piston rod 4 of the plunger pump 2 is at its highest point. The solenoid directional valve 21 needs to be switched to the left state. High-pressure oil is injected into the upper chamber of the plunger pump 2 through the oil inlet, pushing the piston rod 4 downward and compressing the working fluid. Due to the presence of the check valve, the compressed working fluid can only enter the energy storage buffer. During the downward movement of the piston rod 4 of the plunger pump 2, the low-pressure oil in the lower oil chamber of the plunger pump 2 is discharged through the oil outlet. When the piston rod 4 of the plunger pump 2 moves to the lowest point, one compression process ends, and the solenoid directional valve 21 is switched to the right state. At this time, high-pressure oil enters the lower oil chamber of the plunger pump 2, the piston rod 4 moves upward, and the pressure in the booster chamber is less than the working fluid pressure in the cylinder. The working fluid enters the booster chamber, and the oil in the upper oil chamber of the plunger pump 2 is discharged through the oil outlet. When the piston rod 4 of the plunger pump 2 moves to the highest point, one working fluid intake process ends. The above process is repeated, and the state of the solenoid directional valve is continuously switched, in a cyclical manner. During the compression and pressurization process of piston rod 4, the pressure in the pressurization chamber is relatively high, and the resistance is also relatively high. Therefore, under the same oil inlet pressure, the return stroke of piston rod 4 can be shorter than the compression stroke time. The piston movement involves acceleration, deceleration, and stopping, resulting in inconsistent pressure output at different times. When plunger pump 2 is in the pressurization and deceleration phase, the output pressure also begins to decrease because the return stroke time of piston rod 4 is shorter than the compression time. Meanwhile, the piston rod 4 of the other plunger pump 3 is already at its highest point. At this time, the other plunger pump 3 can be controlled by the solenoid directional valve 31 to begin pressurization. The pressurization phases of the two plunger pumps partially overlap, ensuring the continuity and stability of the ultra-high pressure working fluid output. After passing through the energy storage buffer, the working fluid further ensures a continuous and stable output of ultra-high pressure working fluid at the outlet.

[0031] Furthermore, the insulation cylinder 1 includes a cylinder body and a supporting flange 11. The cylinder body has a top-opening structure, and the supporting flange 11 is sealed to the insulation cylinder 1. The plunger pump is vertically fixed on the supporting flange 11 of the insulation cylinder 1, and the pressurization chamber is directly connected to the low-temperature liquid inside the cylinder through the flange through hole.

[0032] Furthermore, the system includes displacement sensors and a controller. The displacement sensors are positioned along the stroke path of the piston rod 4 of each plunger pump 2 and 3, specifically in the middle or end of the piston rod 4's movement trajectory, to detect the position of the piston rod 4 in real time. Both the displacement sensors and the solenoid directional valves are connected to the controller, which in turn is linked to the solenoid directional valves. When the displacement sensor detects that the piston rod 4 of a plunger pump has moved to the end of the pressurization phase (near the end of the stroke) or the return phase (beginning to reset upwards), the controller immediately sends a switching command to the corresponding solenoid directional valve, triggering the pressurization action of the other plunger pump. Through precise timing coordination, seamless switching between the two pumps is achieved, significantly reducing pressure fluctuations and improving system reliability.

[0033] This design combines low-temperature immersion with intelligent control to solve the problem of pressure instability caused by vaporization of low-temperature working fluid during ultra-high pressure output, while ensuring the continuity and stability of the output.

[0034] Furthermore, the piston rod 4 of the plunger pumps 2 and 3 adopts a variable cross-sectional area design, with the cross-sectional area in contact with oil being larger than that in contact with the working fluid. By utilizing the hydraulic amplification effect, the driving oil pressure is converted into a higher working fluid pressure, thereby achieving ultra-high pressure output.

[0035] Furthermore, the insulation cylinder 1 is equipped with a thermometer and a level gauge, which are used to monitor the temperature and level of the cryogenic liquid in real time. The thermometer is installed on the side wall or bottom of the cylinder, in direct contact with the cryogenic liquid, and transmits the temperature data to the external control system through a sensor to ensure that the pressurization chamber is always within the preset low temperature range and to prevent the working fluid from vaporizing. The level gauge is vertically fixed inside the cylinder to detect the liquid level of the cryogenic liquid in real time.

[0036] The above are merely preferred embodiments of the present utility model and do not constitute any limitation on the technical scope of the present utility model. Therefore, any minor modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present utility model shall still fall within the scope of the technical solution of the present utility model.

Claims

1. A high-pressure booster pump for a cryogenic liquid working fluid, characterized in that, include: Insulated cylinder with built-in cryogenic liquid; Two separate, independent plunger pumps, whose booster chambers are completely immersed in the cryogenic liquid within the insulated cylinder; Two solenoid directional valves are connected to two piston pumps respectively. Each solenoid directional valve independently controls the on / off of the input and output ends of the oil chamber of the corresponding piston pump. The pressurization and return actions are achieved by alternately switching the oil circuit. The pressurization phases of the two plunger pumps can be alternated or partially overlapped to ensure continuous output of the ultra-high pressure working fluid.

2. The ultra-high pressure booster pump according to claim 1, characterized in that, It also includes a displacement sensor and a controller. The displacement sensor is set on the piston rod stroke path of the plunger pump to detect the position of the piston rod in real time. The controller is connected to the displacement sensor and the solenoid directional valve. The control logic of the two solenoid directional valves is implemented in the following way: when the displacement sensor detects that the piston rod of a plunger pump is at the end of the pressurization stage or the return stage, the controller sends a switching signal to the corresponding solenoid directional valve to start the pressurization action of the other plunger pump.

3. The ultra-high pressure booster pump according to claim 1 or 2, characterized in that, It also includes an energy storage buffer, which is located inside the insulation cylinder and immersed in a cryogenic liquid. Its input end is connected to the output end of the booster chamber of the two plunger pumps to balance the output pressure fluctuations.

4. The ultra-high pressure booster pump according to claim 1, characterized in that, The cryogenic liquid is either liquid nitrogen or liquid carbon dioxide, and it is the same cryogenic liquid as the pressurizing working fluid.

5. The ultra-high pressure booster pump according to claim 1, characterized in that, In a plunger pump, the cross-sectional area of ​​the piston rod in contact with the oil is larger than the cross-sectional area in contact with the working fluid, in order to achieve a hydraulic amplification effect.

6. The ultra-high pressure booster pump according to claim 1, characterized in that, The insulation cylinder is equipped with a thermometer and a level gauge for real-time monitoring of the temperature and level of the cryogenic liquid.

7. The ultra-high pressure booster pump according to claim 3, characterized in that, The booster chamber of the plunger pump is connected to the energy storage buffer via a one-way valve to ensure unidirectional flow of the working fluid.

8. The ultra-high pressure booster pump according to claim 1, characterized in that, The insulation cylinder includes a cylinder body with a top-open structure. A support flange is fixedly installed on the top of the cylinder body and is sealed to the insulation cylinder. The plunger pumps are vertically installed on the top of the insulation cylinder through the support flange. The support flange has a through hole corresponding to the plunger pump, and the pressurization chamber of the plunger pump enters the insulation cylinder through the through hole.

9. The ultra-high pressure booster pump according to claim 1, characterized in that, The insulated cylinder is equipped with a cooling liquid inlet and a discharge outlet for injecting cryogenic liquid and discharging vaporized liquid.

10. The ultra-high pressure booster pump according to claim 1, characterized in that, The pressurization chamber of the plunger pump draws in the pressurizing working fluid directly from the insulated cylinder.

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