A constant-power superhigh-pressure boosting system and a superhigh-pressure processing device

Abstract

A kind of constant-power superhigh pressure supercharging system and superhigh pressure processing equipment, including low-pressure drive mechanism, superhigh pressure supercharging mechanism and host computer control mechanism, the low-pressure drive mechanism is driven variable pump (2) by motor (1), variable pump (2) import connects oil tank (19), variable pump (2) export is connected with electro-hydraulic reversing valve (6) import by low-pressure check valve (3), electro-hydraulic reversing valve (6) export connects oil tank (19), and the two working ports of electro-hydraulic reversing valve (6) are connected with the two oil ports of the big piston cavity of supercharging cylinder (7) respectively;The superhigh pressure supercharging mechanism is connected with low-pressure drive mechanism by supercharging cylinder (7), and the small plunger cavity of the left side of supercharging cylinder (7) is connected with first water inlet valve (8.1) and first drain valve (9.1), the small plunger cavity of the right side of supercharging cylinder (7) is connected with second water inlet valve (8.2) and second drain valve (9.2), and the outlet of first drain valve (9.1) and second drain valve (9.2) is communicated and is communicated with processing bin (11) by high-pressure check valve (10);Low-pressure pressure sensor (15), first high-pressure pressure sensor (16), second high-pressure pressure sensor (17), displacement sensor (18) output signal to the input end of host computer control mechanism (20).

Description

Technical Field

[0001] This invention relates to the field of ultra-high pressure hydraulic control technology, and in particular to constant power ultra-high pressure boosting technology. Background Technology

[0002] As ultra-high pressure (UHPP) processing technology matures and its applications become more widespread, higher demands are being placed on the efficiency and lifespan of UHPP systems and equipment. During UHPP processing, the load pressure continuously increases. Currently, the hydraulic pumps in UHPP booster systems are mainly fixed-displacement pumps and constant-pressure variable-displacement pumps, resulting in a constant output flow. Therefore, the power of the hydraulic pump and motor must be calculated and selected based on the maximum load pressure. The resulting system only outputs full power at the maximum load pressure; it does not output full power during the booster process from low pressure to maximum pressure, leading to significant power waste. Furthermore, because both fixed-displacement and constant-pressure variable-displacement pumps provide constant flow, and the piston displacement of the booster cylinder is often detected using limit switches, violent cylinder impact occurs during the piston's reciprocating motion.

[0003] Based on the requirements of ultra-high pressure processing, the characteristics of constant power variable pumps—high flow rate at low pressure and low flow rate at high pressure—are well-suited for ultra-high pressure boosting systems. However, the high flow rate at low pressure in constant power variable pumps significantly increases the movement speed of the booster cylinder at low pressure, which in turn increases the movement speed of the high-pressure reciprocating dynamic seal between the small plunger of the booster cylinder and the high-pressure cylinder, exacerbating friction and wear on the seals and reducing their service life. Furthermore, after the boosting and ultra-high pressure processing in the treatment chamber is completed, the ultra-high pressure medium is directly unloaded. This results in significant energy waste, and the instantaneous unloading of pressures of hundreds or thousands of megapascals causes a significant impact on the unloading valves, pipelines, and water tank, which is detrimental to unloading stability and also reduces the service life of components. Summary of the Invention

[0004] The purpose of this invention is to provide a constant power ultra-high voltage boosting system and ultra-high voltage processing equipment, which solves some or all of the technical problems existing in the prior art.

[0005] In a first aspect, the present invention provides a constant power ultra-high pressure boosting system, comprising a low-pressure drive mechanism, an ultra-high pressure boosting mechanism, and a host computer control mechanism. The low-pressure drive mechanism is driven by a motor 1 to drive a variable pump 2. The inlet of the variable pump 2 is connected to an oil tank 19. The outlet of the variable pump 2 is connected to the inlet of an electro-hydraulic directional valve 6 via a low-pressure check valve 3. The outlet of the electro-hydraulic directional valve 6 is connected to the oil tank 19. The two working ports of the electro-hydraulic directional valve 6 are respectively connected to the two oil ports of the large piston chamber of the boosting cylinder 7. A safety valve 5 and an electro-proportional relief valve 4 are connected in parallel between the low-pressure check valve 3 and the electro-hydraulic directional valve 6. The outlets of the safety valve 5 and the electro-proportional relief valve 4 are connected to the oil tank 19.

[0006] The ultra-high pressure boosting mechanism is connected to the low-pressure drive mechanism through the boosting cylinder 7. The small plunger chamber on the left side of the boosting cylinder 7 is connected to the first water inlet valve 8.1 and the first water outlet valve 9.1. The small plunger chamber on the right side of the boosting cylinder 7 is connected to the second water inlet valve 8.2 and the second water outlet valve 9.2. The outlets of the first water outlet valve 9.1 and the second water outlet valve 9.2 are connected and connected to the processing chamber 11 through the high-pressure check valve 10. The unloading valve 14 and the shut-off valve 12 are connected in parallel between the processing chamber 11 and the high-pressure check valve 10. The shut-off valve 12 is connected to the spring accumulator 13.

[0007] The variable pump 2 is a constant power variable pump. The Y port of the variable pump 2 is connected to the control pressure oil. The displacement of the variable pump 2 can be actively adjusted by the proportional solenoid valve 2.1.

[0008] The inlet of the first water inlet valve 8.1 and the inlet of the second water inlet valve 8.2 are connected to the water inlet, and a low-pressure water injection port is provided at one end of the treatment chamber 11;

[0009] Both the unloading valve 14 and the shut-off valve 12 can be electrically controlled. The methods of electrical control include, but are not limited to, direct drive by electromagnet, electric cylinder drive, and indirect drive by electric hydraulic cylinder or pneumatic cylinder.

[0010] A low-pressure sensor 15 is provided between the low-pressure check valve 3 and the electro-hydraulic directional valve 6; a first high-pressure sensor 16 is provided between the processing chamber 11 and the high-pressure check valve 10; a second high-pressure sensor 17 is provided between the shut-off valve 12 and the spring accumulator 13; and a displacement sensor 18 is provided in the booster cylinder 7 to monitor piston displacement. The low-pressure sensor 15, the first high-pressure sensor 16, the second high-pressure sensor 17, and the displacement sensor 18 output signals to the input terminal of the host computer control mechanism 20. The output terminal of the host computer control mechanism 20 sends control signals to the proportional solenoid valve 2.1, the electro-proportional relief valve 4, the electro-hydraulic directional valve 6, the shut-off valve 12, and the unloading valve 14. The host computer control mechanism 20 can be programmed to process the input signals of the sensors through a program and output control signals to switch and control the working state of the electronic control components.

[0011] The spring accumulator 13 is composed of a cylinder 13.2, a piston 13.3, a spring 13.1 and a seal 13.4. The springless chamber of the cylinder 13.2 is provided with an inlet and outlet 13.5. The piston 13.3 can move translationally under the pressure of the spring 13.1 and the springless chamber.

[0012] Secondly, an ultra-high pressure processing device is also provided, which includes the aforementioned constant power ultra-high pressure boosting system.

[0013] Compared with the prior art, the present invention has the following advantages:

[0014] 1. A constant-power variable pump is used as the power source for the ultra-high pressure boosting system. It outputs a large flow rate at low pressure and a small flow rate at high pressure, thus reducing the maximum power of motor 1 and variable pump 2. This allows the ultra-high pressure boosting system to output its full power during the boosting process, eliminating power waste. This invention can be used as an ultra-high pressure processing device.

[0015] 2. After the pressure in the treatment chamber 11 reaches the working pressure and the ultra-high pressure treatment is completed, the shut-off valve 12 is opened to connect the treatment chamber 11 and the spring accumulator 13, completing the partial depressurization of the treatment chamber 11 and the pressurization of the spring accumulator 13. Then, the shut-off valve 12 is closed and the unloading valve 14 is opened to completely depressurize the treatment chamber 11. When pressurizing the treatment chamber 11 again, the shut-off valve 12 is opened first, and the spring accumulator 13 is used to quickly pressurize the treatment chamber 11. Then, the constant power variable pump 2 drives the booster cylinder 7 to pressurize the treatment chamber 11. This realizes the recovery and utilization of ultra-high pressure energy in the treatment chamber 11; reduces the pressure impact of the unloading valve 14 and improves the service life of the components; and realizes the segmented pressurization of the treatment chamber 11. At low pressure, the spring accumulator 13 pressurizes instead of the constant power variable pump 2 pressurizes at low pressure and high flow rate, eliminating the reduction in the life of the reciprocating dynamic seal caused by the rapid displacement of the booster cylinder 7, improving the pressurization efficiency of the treatment chamber 11, and thus improving the overall working efficiency of the equipment.

[0016] 3. By matching the design, changing the parameters such as the stiffness of the spring 13.1, the pre-compression amount, the natural length, and the area of ​​the piston 13.3 of the spring accumulator 13, the low-pressure charging process of the processing chamber 11 can be flexibly adjusted.

[0017] 4. A displacement sensor 18 is used to monitor the piston displacement of the booster cylinder 7 in real time. The electro-hydraulic directional valve 6 is actively controlled by the upper computer control mechanism 20 to switch before the piston of the booster cylinder 7 hits the cylinder. This achieves accurate and flexible matching control between the switching of the electro-hydraulic directional valve 6 and the movement of the piston of the booster cylinder 7, thus eliminating the problem of piston collision in the booster cylinder 7.

[0018] 5. In the hydraulic system of this invention, all control valves are electromagnetically controlled. The variable pump 2 can be controlled by a proportional solenoid valve 2.1. Pressure sensors 15, 16, 17 and displacement sensor 18 are set at key positions in the system to monitor the system pressure status and the movement status of the booster cylinder 7 in real time during the boosting process. Through data acquisition and processing and program control by the host computer control mechanism 20, the system status monitoring and fully automatic control of the boosting process can be realized. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the hydraulic system principle of the constant power ultra-high pressure boosting system of the present invention. Figure 2This is a schematic diagram of the structure and principle of the spring accumulator of the present invention. In the figure: 1-motor; 2-variable pump; 2.1-proportional solenoid valve; 3-low-pressure check valve; 4-electro-proportional relief valve; 5-safety valve; 6-electro-hydraulic directional valve; 7-boost cylinder; 8.1-first inlet valve; 8.2-second inlet valve; 9.1-first drain valve; 9.2-second drain valve; 10-high-pressure check valve; 11-processing chamber; 12-stop valve; 13-spring accumulator; 13.1-spring; 13.2-cylinder; 13.3-piston; 13.4-seal; 13.5-inlet and outlet; 14-unloading valve; 15-low-pressure sensor; 16-first high-pressure sensor; 17-second high-pressure sensor; 18-displacement sensor; 19-oil tank; 20-host computer control mechanism. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described below with reference to the accompanying drawings and embodiments.

[0021] like Figure 1 , Figure 2 As shown, this invention is a constant power ultra-high pressure boosting system, including a low-pressure drive mechanism, an ultra-high pressure boosting mechanism, and a host computer control mechanism. The low-pressure drive mechanism is driven by a motor 1 that drives a variable pump 2. The inlet of the variable pump 2 is connected to an oil tank 19, and the outlet of the variable pump 2 is connected to the inlet of an electro-hydraulic directional valve 6 via a low-pressure check valve 3. The outlet of the electro-hydraulic directional valve 6 is connected to the oil tank 19. The two working ports of the electro-hydraulic directional valve 6 are respectively connected to the two oil ports of the large piston chamber of the booster cylinder 7. A safety valve 5 and an electro-proportional relief valve 4 are connected in parallel between the low-pressure check valve 3 and the electro-hydraulic directional valve 6. For example, the outlet of the overflow valve 4 is connected to the oil tank 19; the ultra-high pressure boosting mechanism is connected to the low pressure drive mechanism through the boosting cylinder 7. The small plunger chamber on the left side of the boosting cylinder 7 is connected to the first water inlet valve 8.1 and the first drain valve 9.1, and the small plunger chamber on the right side of the boosting cylinder 7 is connected to the second water inlet valve 8.2 and the second drain valve 9.2. The outlets of the first drain valve 9.1 and the second drain valve 9.2 are connected and connected to the processing chamber 11 through the high pressure check valve 10. The unloading valve 14 and the shut-off valve 12 are connected in parallel between the processing chamber 11 and the high pressure check valve 10. The shut-off valve 12 is connected to the spring accumulator 13.

[0022] like Figure 1 As shown, variable pump 2 is a constant power variable pump. The Y port of variable pump 2 is connected to control pressure oil. The displacement of variable pump 2 can be actively adjusted by proportional solenoid valve 2.1.

[0023] like Figure 1 As shown, the inlet of the first water inlet valve 8.1 and the inlet of the second water inlet valve 8.2 are connected to the water inlet, and a low-pressure water inlet is provided at one end of the treatment chamber 11.

[0024] like Figure 1As shown, both the unloading valve 14 and the shut-off valve 12 can be electrically controlled. The implementation of the electrical control includes, but is not limited to, direct drive by electromagnet, electric cylinder drive, and indirect drive by electric hydraulic cylinder or pneumatic cylinder.

[0025] like Figure 1 , Figure 2 As shown, a low-pressure sensor 15 is provided between the low-pressure check valve 3 and the electro-hydraulic directional valve 6; a first high-pressure sensor 16 is provided between the processing chamber 11 and the high-pressure check valve 10; a second high-pressure sensor 17 is provided between the shut-off valve 12 and the spring accumulator 13; and a displacement sensor 18 is provided in the booster cylinder 7 to monitor piston displacement. The low-pressure sensor 15, the first high-pressure sensor 16, the second high-pressure sensor 17, and the displacement sensor 18 output signals to the input terminal of the host computer control mechanism 20. The output terminal of the host computer control mechanism 20 sends control signals to the proportional solenoid valve 2.1, the electro-proportional relief valve 4, the electro-hydraulic directional valve 6, the shut-off valve 12, and the unloading valve 14. The host computer control mechanism 20 can be programmed to process the input signals of the sensors through program calculations and output control signals to switch and control the working state of the electronic control components.

[0026] like Figure 1 , Figure 2 As shown, the spring accumulator 13 consists of a cylinder 13.2, a piston 13.3, a spring 13.1, and a seal 13.4. The springless chamber of the cylinder 13.2 is provided with an inlet and outlet 13.5. The piston 13.3 can move translationally under the pressure of the spring 13.1 and the springless chamber.

[0027] like Figure 1 , Figure 2 As shown, the working process of this invention is as follows:

[0028] Step 1: When pressurizing the processing chamber 11 for the first time, quickly fill the processing chamber 11 with water through the low-pressure water inlet. The pressure in both the spring accumulator 13 and the processing chamber 11 is atmospheric. The variable pump 2Y port is connected to the control pressure oil. The upper computer control mechanism 20 sends a signal to adjust the opening of the proportional solenoid valve 2.1, thereby reducing the displacement of the variable pump 2. The specific value of the displacement is calculated and determined according to the piston displacement requirement of the booster cylinder 7 and the speed of the motor 1. The direction of the output liquid flow of the variable pump 2 is controlled by the electro-hydraulic reversing valve 6. The variable pump 2 drives the booster cylinder 7 to reciprocate with a small flow rate, completing the first pressurization of the processing chamber 11. The time of this pressurization process is longer than the target time designed by the system. After the first pressurization is completed, ultra-high pressure treatment is carried out, that is, the processing chamber 11 is pressurized for a certain period of time. Then, the processing chamber 11 is depressurized and the items that have completed ultra-high pressure treatment are taken out of the processing chamber 11.

[0029] Step Two: When depressurizing the treatment chamber 11, first open the shut-off valve 12 to connect the treatment chamber 11 and the spring accumulator 13. The pressure in the treatment chamber 11 is greater than that in the spring accumulator 13. The liquid in the treatment chamber 11 flows into the spring accumulator 13 through the shut-off valve 12, causing the pressure in the treatment chamber 11 to decrease and the pressure in the spring accumulator 13 to increase. The piston 13.3 moves towards the spring 13.1, compressing the spring 13.3 until the pressure in the treatment chamber 11 equals the pressure in the spring accumulator 13. Then, close the shut-off valve 12. At this point, partial depressurization of the treatment chamber 11 (first depressurization) and pressurization of the spring accumulator 13 are completed. Then, open the depressurization valve 14 to depressurize the pressure in the treatment chamber 11 to atmospheric pressure (secondary depressurization). During the first depressurization, the charging pressure, charging liquid volume, and piston stroke of the spring accumulator 13 can be flexibly adjusted by adjusting parameters such as the stiffness of the spring 13.1, the pre-compression amount, the natural length, and the area of ​​the piston 13.3.

[0030] Step 3: When pressurizing the treatment chamber 11 for the second time, close the unloading valve 14, first quickly fill the treatment chamber 11 with water through the low-pressure water inlet, then open the shut-off valve 12 to connect the spring accumulator 13 and the treatment chamber 11. The pressure in the spring accumulator 13 is greater than that in the treatment chamber 11, and the liquid flows into the treatment chamber 11 through the shut-off valve 12 until the pressure in the treatment chamber 11 is equal to the pressure in the spring accumulator 13. Then close the shut-off valve 12 to complete the first pressurization of the treatment chamber 11. Then start the motor 1, and use the variable pump 2 to output liquid flow through the low-pressure check valve 3 and the electro-hydraulic reversing valve 6 to drive the booster cylinder 7 to reciprocate, injecting liquid flow into the treatment chamber 11 and raising the pressure in the treatment chamber 11 to the target pressure, thus completing the second pressurization of the treatment chamber 11. In this step, since the processing chamber 11 is first pressurized by the spring accumulator 13, the load pressure of the variable pump 2 at the start of operation is high pressure. The output flow of the variable pump 2 is automatically adjusted to a smaller flow rate by constant power. That is, the first pressurization by the spring accumulator 13 causes the variable pump 2 to skip the low-pressure, high-flow-rate output stage when it starts working. Therefore, the piston of the booster cylinder 7 does not have a rapid displacement condition, eliminating the problem of reduced lifespan of the reciprocating dynamic seal of the booster cylinder 7 due to friction caused by rapid movement. In addition, the starting flow rate of the variable pump 2 during the second pressurization can be flexibly and controllably adjusted by matching the parameters of the spring accumulator 13, the variable pump 2, and the booster cylinder 7.

[0031] Step 4: Complete the ultra-high pressure holding process, and then repeat Step 2 and Step 3 to complete the first pressurization, second pressurization, pressure holding process, first depressurization, and second depressurization of the multiple treatment chambers 11.

[0032] Furthermore, the host computer control mechanism 20 collects the piston displacement of the booster cylinder 7 in real time through the displacement sensor 18, and actively controls the electro-hydraulic directional valve 6 to switch before the piston of the booster cylinder 7 collides with the cylinder, thereby achieving accurate and flexible matching control between the switching of the electro-hydraulic directional valve 6 and the movement of the piston of the booster cylinder 7, and eliminating the problem of piston collision of the booster cylinder 7.

[0033] Furthermore, all control valves in the hydraulic system of this invention are electromagnetically controlled. The variable pump 2 can be controlled by a proportional solenoid valve 2.1. Pressure sensors 16 and 17 and displacement sensor 18 are set at key positions in the system to monitor the system pressure status and the movement status of the booster cylinder 7 in real time during the boosting process. Through data acquisition and processing and program control by the host computer control mechanism 20, the system status monitoring and fully automatic control of the boosting process can be realized.

[0034] Secondly, the present invention also provides an ultra-high pressure processing device, the ultra-high pressure device including the above-mentioned constant power ultra-high pressure boosting system.

[0035] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Additionally, the terms "front," "back," "left," "right," "upper," and "lower" in this document refer to the placement shown in the accompanying drawings.

[0036] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A constant power superhigh pressure boosting system comprising a low pressure driving mechanism, a superhigh pressure boosting mechanism and an upper computer control mechanism, characterized in that The low-pressure drive mechanism is driven by a motor (1) to drive a variable pump (2). The inlet of the variable pump (2) is connected to the oil tank (19). The outlet of the variable pump (2) is connected to the inlet of the electro-hydraulic directional valve (6) via a low-pressure check valve (3). The outlet of the electro-hydraulic directional valve (6) is connected to the oil tank (19). The two working ports of the electro-hydraulic directional valve (6) are respectively connected to the two oil ports of the large piston chamber of the booster cylinder (7). The low-pressure check valve (3) and the electro-hydraulic directional valve (6) are connected in parallel to a safety valve (5) and an electro-proportional relief valve (4). The outlets of the safety valve (5) and the electro-proportional relief valve (4) are connected to the oil tank (19). The ultra-high pressure boosting mechanism is connected to the low pressure drive mechanism through the boosting cylinder (7). The small plunger chamber on the left side of the boosting cylinder (7) is connected to the first water inlet valve (8.1) and the first drain valve (9.1). The small plunger chamber on the right side of the boosting cylinder (7) is connected to the second water inlet valve (8.2) and the second drain valve (9.2). The outlets of the first drain valve (9.1) and the second drain valve (9.2) are connected and connected to the processing chamber (11) through the high pressure check valve (10). The processing chamber (11) and the high pressure check valve (10) are connected in parallel with the unloading valve (14) and the shut-off valve (12). The shut-off valve (12) is connected to the spring accumulator (13). The variable pump (2) is a constant power variable pump. The Y port of the variable pump (2) is connected to the control pressure oil. The displacement of the variable pump (2) is actively adjusted by the proportional solenoid valve (2.1). A low-pressure sensor (15) is provided between the low-pressure check valve (3) and the electro-hydraulic directional valve (6). A first high-pressure sensor (16) is provided between the processing chamber (11) and the high-pressure check valve (10). A second high-pressure sensor (17) is provided between the shut-off valve (12) and the spring accumulator (13). A displacement sensor (18) is provided in the booster cylinder (7) to monitor the piston displacement. The low-pressure sensor (15), the first high-pressure sensor (16), the second high-pressure sensor (17), and the displacement sensor (18) output signals to the input terminal of the host computer control mechanism (20). The output terminal of the host computer control mechanism (20) sends control signals to the proportional solenoid valve (2.1), the electro-proportional relief valve (4), the electro-hydraulic directional valve (6), the shut-off valve (12), and the unloading valve (14). The host computer control mechanism (20) can be programmed to process the input signals of the low-pressure sensor (15), the first high-pressure sensor (16), the second high-pressure sensor (17), and the displacement sensor (18) through a program. The inlet of the first water inlet valve (8.1) and the inlet of the second water inlet valve (8.2) are connected to the water inlet, and a low-pressure water inlet is provided at one end of the treatment chamber (11); Both the unloading valve (14) and the shut-off valve (12) are electrically controlled. The methods of implementation of the electrical control include direct drive by electromagnet, electric cylinder drive, and indirect drive by electric hydraulic cylinder or pneumatic cylinder.

2. The constant power ultra-high voltage booster system according to claim 1, characterized in that: The spring accumulator (13) consists of a cylinder (13.2), a piston (13.3), a spring (13.1), and a seal (13.4). The springless cavity of the cylinder (13.2) is provided with an inlet and outlet (13.5). The piston (13.3) can move in translation under the pressure of the spring (13.1) and the springless cavity.

3. An ultra-high pressure processing device, characterized in that: The system includes the constant power ultra-high pressure boosting system according to any one of claims 1-2.

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