High-pressure jet system

Abstract

The invention relates to the technical field of burr cleaning, in particular to a high-pressure jet system which comprises a high-pressure pump, a liquid supply pipeline, a nozzle, a pulse pressurizing mechanism and a controller, and one end of the liquid supply pipeline communicates with the output end of the high-pressure pump; the nozzle communicates with the end, away from the high-pressure pump, of the liquid supply pipeline. The pulse pressurizing mechanism is arranged on the liquid supply pipeline; and the controller is electrically connected with the high-pressure pump and the pulse pressurization mechanism and used for controlling the movement frequency of the pulse pressurization mechanism to be matched with the pressure pulsation frequency of the high-pressure pump so that a medium sprayed out of the nozzle can be in a pulse pressurization state. Pulse pressurization can be obtained with small energy consumption, and the impact damage capacity to hard burrs is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of burr cleaning, and particularly relates to a high-pressure jet system. BACKGROUND

[0002] In the machining process of metal parts, deep and long hole structure is a common structure, and burrs are prone to occur at the intersection of the deep and long hole. The existence of these burrs will seriously affect the assembly accuracy, use performance and service life of the metal parts, and therefore the effective removal of deep hole burrs is a key problem in the field of metal part machining.

[0003] At present, the high-pressure jet deburring technology has been widely applied in industrial production due to its high degree of automation, strong adaptability, no chemical pollution and other advantages. The existing high-pressure jet deburring equipment includes a high-pressure pump, a liquid supply pipeline and a nozzle. The high-pressure water generated by the high-pressure pump is directly provided to the nozzle through the liquid supply pipeline. The jet hole direction of the nozzle is aligned with the burr position of the workpiece. The nozzle continuously sprays high-pressure water outward, and the impact pressure of the high-pressure jet is used to remove the burrs of the workpiece.

[0004] However, the existing high-pressure jet deburring equipment has obvious deficiencies. The high-pressure water jet is divided into two stages: water hammer pressure stage and stagnation pressure stage. The water hammer pressure is much higher than the stagnation pressure, that is, the pressure acting on the burr surface during continuous jetting of the nozzle is lower than the pressure during the initial stage of the jet. At the same time, the pressure jetted by the nozzle is inevitably lower than the pressure generated by the high-pressure pump due to the along-path resistance loss of the system, and therefore the pressure acting on the burr surface is usually difficult to reach the design pressure. The existing equipment does not have a pressure boosting function, and it is more difficult to reach the burr position in the deep hole. If the jetting pressure of the nozzle cannot reach the design pressure, the intersection hole burrs cannot be completely removed. The traditional technology can only increase the jetting pressure by selecting a high-pressure pump with higher pressure, but this will cause the energy consumption of the system to increase, and the entire pipeline is subjected to high pressure, which is prone to leakage.

[0005] In addition, the existing high-pressure water deburring equipment does not have a pulse function and cannot fully utilize the high impact pressure characteristics of the initial stage of the jet. The high-pressure pump itself has a large pressure pulsation, but the existing technology cannot effectively utilize this pressure pulsation characteristic, but instead regards it as an unfavorable factor for system stability. The pulse jet equipment applied in other fields usually generates pulses by using self-excitation pulses or additional excitation equipment, and cannot utilize the pressure pulsation of the high-pressure pump itself, which increases the complexity and energy consumption of the system.

[0006] Especially for hard burrs at the intersection of the deep hole, the impact force of the traditional continuous jet is often insufficient to achieve effective removal, which requires a long time of continuous flushing, which not only is low in efficiency, but also is high in energy consumption. SUMMARY

[0007] The application provides a high-pressure jet system which can convert pressure pulsation of a high-pressure pump into a pressurized power source, so that pulse pressurization can be obtained with small energy consumption, and the impact damage capacity on hard burrs is improved.

[0008] The application provides a high-pressure jet system for burr removal, which comprises a high-pressure pump, a liquid supply pipeline, one end of the liquid supply pipeline being in communication with an output end of the high-pressure pump, a nozzle, the nozzle being in communication with an end of the liquid supply pipeline away from the high-pressure pump, a pulse pressurization mechanism, the pulse pressurization mechanism being arranged on the liquid supply pipeline, and a controller, the controller being electrically connected with the high-pressure pump and the pulse pressurization mechanism respectively, and being used for controlling the motion frequency of the pulse pressurization mechanism to match the pressure pulsation frequency of the high-pressure pump, so that the medium sprayed by the nozzle is in a pulse pressurization state.

[0009] In a possible implementation manner, the pulse pressurization mechanism comprises a shell having a cavity, the shell being connected into the liquid supply pipeline, a piston being slidingly arranged in the cavity, the piston being capable of reciprocating in the cavity to change the volume of the cavity, a driving assembly, an output end of the driving assembly being connected with the piston, and the driving assembly being used for driving the piston to reciprocate, and a first one-way valve being arranged on the liquid supply pipeline and located at an input port of the shell.

[0010] In a possible implementation manner, the pulse pressurization mechanism further comprises a second one-way valve, the second one-way valve being arranged in the liquid supply pipeline and located at an output port of the shell.

[0011] In a possible implementation manner, the piston is provided with a transmission hole, the driving assembly comprises an electric motor, a cam being arranged at an output end of the electric motor, the cam being arranged in the transmission hole and being used for driving the piston to reciprocate, and the motion frequency of the electric motor matches the frequency of the high-pressure pump.

[0012] In a possible implementation manner, the controller is configured to control the output pressure of the high-pressure pump to be in a rising stage in the process of reducing the volume of the cavity, and control the output pressure of the high-pressure pump to be in a falling stage in the process of increasing the volume of the cavity.

[0013] In a possible implementation manner, the controller comprises a pressure detection unit, the pressure detection unit being used for detecting the pressure pulsation frequency of the high-pressure pump.

[0014] In a possible implementation manner, the distance between the pulse pressurization mechanism and the nozzle is less than 1 meter.

[0015] In a possible implementation manner, the nozzle is a ceramic nozzle.

[0016] In a possible implementation manner, the nozzle comprises a pipe body, one end of the pipe body being in communication with the liquid supply pipeline, the other end of the pipe body being closed, a plurality of groups of jet holes being arranged on the side wall of the pipe body, and the plurality of groups of jet holes being distributed along the axial direction of the pipe body.

[0017] In one possible implementation, the axis of the injection hole forms a 135° angle with the axis of the pipe body.

[0018] In one possible implementation, there are three sets of injection holes, with two injection holes in each set.

[0019] Secondly, the present invention provides a burr removal method using the above-mentioned high-pressure jet system, comprising the following steps: starting a high-pressure pump to generate a high-pressure liquid with pressure pulsation; and controlling the movement frequency of the pulse boosting mechanism to synchronize with the pressure pulsation frequency of the high-pressure pump through a controller.

[0020] In one possible implementation, as the output pressure of the high-pressure pump increases, the pressure of the pulse booster mechanism increases synchronously; as the output pressure of the high-pressure pump decreases, the pressure of the pulse booster mechanism decreases synchronously.

[0021] This invention provides a high-pressure jet system in which a pulse booster mechanism on the liquid supply line works in conjunction with a controller to match the movement frequency of the pulse booster mechanism with the pressure pulsation frequency of the high-pressure pump, thus solving the problem of insufficient impact force in existing high-pressure jet deburring equipment. The pressure pulsations generated by the high-pressure pump during operation are amplified by the pulse booster mechanism. When the output pressure of the high-pressure pump is in the rising phase, the pulse booster mechanism synchronously boosts the pressure, resulting in the pressure changes of the two booster sources being superimposed in phase. The controller monitors the pressure pulsation characteristics of the high-pressure pump and adjusts the operating parameters of the pulse booster mechanism to ensure that the frequencies of the two are consistent, thereby converting the original pressure pulsations of the high-pressure pump into the boosting power of the system. The pulse booster mechanism periodically boosts the high-pressure liquid flowing through it, causing the jet pressure obtained at the nozzle to significantly exceed the output pressure of the high-pressure pump operating alone. The jet after pulse boosting exhibits a distinct pressure peak characteristic, approaching the water hammer pressure effect in the initial stage of the jet, and can generate a strong, instantaneous impact when acting on the burr surface. The mechanism by which this high-pressure pulse destroys burrs at deep hole intersections primarily lies in the fact that the instantaneous high pressure can quickly overcome the shear strength of the burr material, disrupting the interface between the burr and the workpiece substrate, thus achieving effective burr removal. Compared to the traditional continuous jet method that relies on relatively low stagnation pressure for prolonged scouring, the pulsed pressurized jet significantly shortens the burr removal time through instantaneous high-pressure impact, making it particularly suitable for treating high-hardness burrs. This technical solution also avoids the increased system energy consumption and pipeline leakage risks associated with simply increasing the pressure level of the high-pressure pump, achieving a significant improvement in jet impact capability while maintaining a constant system base pressure. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in this invention or 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 some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0023] Figure 1 This is a schematic diagram of a high-pressure jet system provided by the present invention.

[0024] Figure 2 This is a cross-sectional structural diagram of a housing, piston, and cam provided by the present invention.

[0025] Figure 3 This is a schematic diagram of the structure of a nozzle provided by the present invention.

[0026] Figure label: 1. High-pressure pump; 2. Liquid supply pipeline; 3. Nozzle; 31. Pipe body; 32. Injection hole; 4. Pulse booster mechanism; 41. Housing; 411. Cavity; 412. Input port; 413. Output port; 42. Piston; 421. Transmission hole; 43. First check valve; 44. Second check valve; 45. Motor; 46. Cam; 5. Controller. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0028] The following is combined Figures 1 to 3 This invention describes a high-pressure jet system, specifically a high-pressure jet system for deburring, comprising a high-pressure pump 1, a liquid supply line 2, a nozzle 3, a pulse boosting mechanism 4, and a controller 5, wherein: One end of the liquid supply line 2 is connected to the output end of the high-pressure pump 1.

[0029] Nozzle 3 is connected to the end of the liquid supply line 2 away from the high-pressure pump 1.

[0030] The pulse boosting mechanism 4 is located on the liquid supply line 2.

[0031] The controller 5 is electrically connected to the high-pressure pump 1 and the pulse boosting mechanism 4 respectively, and is used to control the movement frequency of the pulse boosting mechanism 4 to match the pressure pulsation frequency of the high-pressure pump 1, so that the medium sprayed from the nozzle 3 is in a pulse boosting state.

[0032] In this invention, the pulse boosting mechanism 4 installed on the liquid supply pipeline 2 works in conjunction with the controller 5 to match the movement frequency of the pulse boosting mechanism 4 with the pressure pulsation frequency of the high-pressure pump 1, thus solving the problem of insufficient impact force in existing high-pressure jet deburring equipment. The pressure pulsation generated by the high-pressure pump 1 during operation is amplified by the pulse boosting mechanism 4. When the output pressure of the high-pressure pump 1 is in the rising phase, the pulse boosting mechanism 4 synchronously performs boosting operation, and the pressure changes of the two boosting sources are superimposed in phase. The controller 5 monitors the pressure pulsation characteristics of the high-pressure pump 1 and adjusts the operating parameters of the pulse boosting mechanism 4 to ensure that the frequencies of the two remain consistent, thereby converting the original pressure pulsation of the high-pressure pump 1 into the boosting power of the system. The pulse boosting mechanism 4 periodically boosts the high-pressure liquid flowing through it, making the jet pressure obtained at the nozzle 3 significantly exceed the output pressure of the high-pressure pump 1 when it operates alone. The jet after pulse boosting has obvious pressure peak characteristics, approaching the water hammer pressure effect in the initial stage of the jet, and can generate a strong instantaneous impact when acting on the burr surface. The mechanism by which this high-pressure pulse destroys burrs at deep hole intersections primarily lies in the fact that the instantaneous high pressure can quickly overcome the shear strength of the burr material, disrupting the interface between the burr and the workpiece substrate, thus achieving effective burr removal. Compared to the traditional continuous jet method that relies on relatively low stagnation pressure for prolonged scouring, the pulsed pressurized jet significantly shortens the burr removal time through instantaneous high-pressure impact, making it particularly suitable for treating high-hardness burrs. This technical solution also avoids the increased system energy consumption and pipeline leakage risks associated with simply increasing the pressure rating of the high-pressure pump, achieving a significant improvement in jet impact capability while maintaining a constant system base pressure.

[0033] Specifically, high-pressure pump 1 provides the system with basic high-pressure liquid through supply line 2, and pulse booster mechanism 4, as an intermediate link, periodically boosts the pressure of the flowing high-pressure liquid. Controller 5 is electrically connected to both high-pressure pump 1 and pulse booster mechanism 4, monitoring the pressure pulsation characteristics of high-pressure pump 1 in real time and adjusting the operating frequency of pulse booster mechanism 4 to ensure that their operating frequencies match. Nozzle 3 is connected to the end of supply line 2 furthest from high-pressure pump 1, receiving the pulse-boosted high-pressure liquid and forming a jet.

[0034] In one specific embodiment, for removing metal burrs at intersections within deep holes of machined parts, traditional continuous high-pressure jets often struggle to generate sufficient impact force at the end of the deep hole to remove hard burrs due to pressure loss along the jet and limitations imposed by stagnation pressure. This invention, through pulsed pressurization technology, maintains a high impact pressure even when the jet reaches the burr location. Utilizing the water hammer effect of the pulsed jet to instantly generate high pressure, it effectively breaks the root connection of the burr, achieving complete removal.

[0035] In related technologies, existing high-pressure jet deburring equipment typically uses a continuous high-pressure jet generated by a high-pressure pump 1 to remove burrs. The jet pressure of such equipment mainly depends on the output pressure of the high-pressure pump 1, and the jet characteristic is a continuous and stable high-pressure water flow. The pressure acting on the burr surface is primarily a relatively low stagnation pressure. In this embodiment of the invention, the pulse boosting mechanism 4 performs secondary pressurization on top of the base pressure of the high-pressure pump 1. Through frequency matching control by the controller 5, effective pressure superposition is achieved. The pulse-boosted jet can generate an instantaneous impact pressure far exceeding that of a continuous jet, fully utilizing the water hammer pressure effect in the initial stage of the jet and significantly improving the impact and destructive capability against hard burrs.

[0036] like Figure 2 As shown, in some embodiments, the pulse boosting mechanism 4 includes: a housing 41 having a cavity 411, the housing 41 being connected to the liquid supply line 2; a piston 42 slidably disposed within the cavity 411, the piston 42 being reciprocating along the cavity 411 to change the volume of the cavity 411; a drive assembly, the output end of the drive assembly being connected to the piston 42 for driving the piston 42 to reciprocate; and a first one-way valve 43 disposed on the liquid supply line 2 and located at the inlet 412 of the housing 41.

[0037] In this invention, the reciprocating motion of the piston 42 within the housing 41 alters the volume of the cavity 411. Combined with the unidirectional flow guidance of the first one-way valve 43, this effectively amplifies the output pressure of the high-pressure pump 1. When the piston 42 moves in the compression direction, the volume of the cavity 411 decreases, the liquid inside is compressed, and the pressure rises sharply. At this time, the first one-way valve 43 closes to prevent the high-pressure liquid from flowing back. The high-pressure liquid generated by the compression flows through the outlet 413 of the housing 41 to the nozzle 3. The jet pressure obtained by the nozzle 3 is the superposition of the output pressure of the high-pressure pump 1 and the compression pressure increase of the cavity. When the piston 42 moves in the expansion direction, the volume of the cavity 411 increases, the pressure inside the cavity decreases, and the first one-way valve 43 opens, allowing the high-pressure liquid in the supply line 2 to replenish the cavity 411 in preparation for the next compression. The reciprocating motion of the piston 42 causes the volume of the cavity 411 to change periodically, corresponding to periodic pressure fluctuations. After being guided and controlled by the one-way valve, this results in a distinct pulse jet characteristic at the nozzle 3. This pulsed characteristic gives the jet intermittent high-pressure impact and low-pressure interval when impacting burrs. The powerful impact during the high-pressure phase can quickly destroy the connection at the root of the burr, while the low-pressure interval provides time for pressure release in the impact area. This avoids continuous high pressure impact on nozzle 3 and pipeline system, extending the service life of the equipment. At the same time, the pulsed impact method has a better burr removal effect compared to continuous jet.

[0038] Specifically, the housing 41 is connected to the liquid supply line 2, forming an essential channel for the liquid. Its internal cavity 411 provides working space for liquid pressurization. The piston 42 is slidably disposed within the cavity 411 and can reciprocate along the axial direction of the cavity 411. The displacement of the piston 42 directly changes the effective volume of the cavity 411. The output end of the drive assembly is connected to the piston 42, providing the driving force required for the reciprocating motion of the piston 42. The first one-way valve 43 is disposed on the liquid supply line 2 and located at the inlet 412 of the housing 41, preventing liquid from flowing back towards the high-pressure pump 1 during the compression stroke of the piston 42.

[0039] In one specific embodiment, when processing minute burrs on precision mechanical parts, it is necessary to precisely control the impact force of the jet to avoid damaging the workpiece surface. The piston 42-type pulse boosting mechanism 4 can precisely control the boosting amplitude and duration of each pulse by adjusting the stroke and movement frequency of the piston 42. When the piston 42 moves inward, the volume of the cavity 411 decreases, generating boosting pressure; when it moves outward, the volume of the cavity 411 increases, forming a low-pressure liquid absorption state, thus creating a regular pressure pulse output.

[0040] In this embodiment of the invention, the piston 42-type pulse boosting mechanism 4 has a relatively simple structure. It directly achieves pressure changes through mechanical movement, with a fast response speed and adjustable boosting amplitude. The first one-way valve 43 ensures the one-way nature of the boosting process, avoids the loss of boosting effect caused by liquid backflow, and provides necessary flow channel control for the liquid suction stroke of the piston 42.

[0041] like Figure 1 As shown, in some embodiments, the pulse boosting mechanism 4 further includes a second one-way valve 44, which is disposed in the liquid supply line 2 and located at the output port 413 of the housing 41.

[0042] In this invention, the second one-way valve 44, located at the output port 413 of the housing 41, only opens when the pressure difference between its two ends reaches a preset value, thus achieving precise control of the pulsed jet. When the piston 42 is in the compression stroke, the volume of the cavity 411 decreases, causing the pressure inside the cavity to rise sharply. The pressure difference across the second one-way valve 44 gradually increases. When the pressure difference reaches the preset opening value, the second one-way valve 44 opens, allowing the pressurized high-pressure liquid to flow towards the nozzle 3. At this time, the nozzle 3 ejects a high-pressure jet. The preset pressure difference ensures that liquid is allowed to flow out only when sufficient pressurization is achieved, guaranteeing that the impact pressure of the jet meets the design requirements. When the piston 42 is in the return stroke expansion, the pressure in the cavity 411 decreases, and the pressure difference across the second one-way valve 44 decreases below the preset value. The one-way valve automatically closes, preventing the liquid from continuing to flow to the nozzle 3, and the nozzle 3 stops ejecting. This pressure difference-based opening and closing mechanism makes the jet exhibit obvious pulse characteristics, namely, the alternation of the high-pressure injection phase and the stop injection phase. Compared to continuous spraying, pulse jetting has a stronger impact and destructive force. High-pressure pulses can concentrate energy to instantly impact the root of the burr, effectively destroying the connection interface between the burr and the workpiece. The interval between stopping the spraying provides pressure release time for the impact area, avoiding continuous high pressure on the equipment and extending the service life of the nozzle 3 and the pipeline system.

[0043] In this embodiment of the invention, the addition of the second one-way valve 44 establishes complete flow direction control, ensuring that all the energy from compression and pressurization is used to propel the liquid forward, thus avoiding energy loss. The dual one-way valve configuration allows the system to maintain a stable pressurization effect at various operating frequencies, significantly improving the efficiency and stability of pulse pressurization.

[0044] like Figure 2 As shown, in some embodiments, the piston 42 is provided with a transmission hole 421, and the driving component includes: a motor 45; a cam 46, which is disposed at the output end of the motor 45 and disposed in the transmission hole 421, for driving the piston 42 to reciprocate; wherein, the movement frequency of the motor 45 is matched with the frequency of the high-pressure pump 1.

[0045] In this invention, the transmission hole 421 on the piston 42 cooperates with the cam 46 at the output end of the motor 45, realizing the precise conversion of the rotational motion of the motor 45 into the reciprocating motion of the piston 42. Since the high-pressure pump 1 is also driven by the motor 45, its pressure pulsation characteristics can maintain a high degree of consistency with the pressure pulsation generated by the motor 45 driving the piston 42 in the pulse boosting mechanism 4. The precise adjustability of the motor 45 speed allows the frequency of the reciprocating motion of the piston 42 to be accurately matched with the pressure pulsation frequency of the high-pressure pump 1. When the output pressure of the high-pressure pump 1 reaches its peak, the cam 46 drives the piston 42 to be in the compression stroke, and the pressure increment generated by the reduction in the volume of the cavity 411 is superimposed on the peak pressure of the high-pressure pump 1. When the output pressure of the high-pressure pump 1 is at a low point, the piston 42 is in the expansion stroke, preparing for the next boosting cycle. Compared with the method of using hydraulic cylinders, pneumatic cylinders or other drive components to drive the reciprocating motion of the piston 42, the solution of the motor 45 driving the cam 46 has the advantages of fast response speed, high control accuracy, and good synchronization. The speed control precision of motor 45 can reach a very high level, enabling precise synchronization with the pressure pulsation of high-pressure pump 1, thus avoiding the need for a complex synchronization controller 5 and feedback adjustment mechanism. The cam 46 transmission structure is simple and reliable, with high transmission efficiency and low maintenance cost, achieving more precise and simpler synchronization control, ensuring the maximization of pulse boosting effect and the stability of system operation.

[0046] Specifically, the transmission hole 421 on the piston 42 provides a sliding channel for the cam 46. When the cam 46 rotates within the transmission hole 421, its eccentric structure drives the piston 42 to reciprocate axially along the cavity 411. The motor 45, as a power source, provides stable and controllable rotational power. The rotational speed of the motor 45 directly determines the rotational frequency of the cam 46, thereby controlling the reciprocating frequency of the piston 42. The shape design of the cam 46 determines the displacement curve and velocity variation law of the piston 42.

[0047] In this embodiment of the invention, the motor 45 drive has the advantages of high control precision and fast response speed, enabling precise frequency and phase control. The cam 46 transmission mechanism has a simple and reliable structure, and its geometric design allows for various motion curves, providing a flexible solution for different application needs. The matching of the motor 45 frequency with the high-pressure pump 1 frequency ensures the coordinated operation of the two power sources.

[0048] Optionally, the motor 45 can also drive the piston 42 to reciprocate through a crankshaft connecting rod structure.

[0049] In some embodiments, the controller 5 is configured to: control the output pressure of the high-pressure pump 1 to be in an increasing phase during the process of reducing the volume of the cavity 411; and control the output pressure of the high-pressure pump 1 to be in a decreasing phase during the process of increasing the volume of the cavity 411.

[0050] In this invention, the controller 5 maximizes the pulse boosting effect through precise timing control. During the reduction of the cavity 411 volume, the controller controls the output pressure of the high-pressure pump 1 to be in an increasing phase; during the increase of the cavity 411 volume, the controller controls the output pressure of the high-pressure pump 1 to be in a decreasing phase. This in-phase coordinated control ensures that the pressure changes of the two boosting sources follow the same trend, achieving effective pressure superposition rather than mutual cancellation.

[0051] Specifically, the controller 5 monitors the position of the piston 42 and the pressure status of the high-pressure pump 1. When the piston 42 moves inward and reduces the volume of the cavity 411, the controller simultaneously controls the high-pressure pump 1 to increase the output pressure. The two pressurizing effects are superimposed to produce a higher peak pressure. When the piston 42 moves outward and increases the volume of the cavity 411, the controller correspondingly controls the high-pressure pump 1 to reduce the output pressure to avoid excessive pressure difference in the low-pressure stage.

[0052] In one specific embodiment, removing stubborn burrs inside a deep hole requires the jet to have a sufficiently high peak pressure to overcome frictional resistance and generate an effective impact. Through precise timing matching by the controller 5, the pressure peak of the high-pressure pump 1 and the compression peak of the pulse booster mechanism 4 occur simultaneously, generating a superimposed pressure that far exceeds the capability of a single booster source, maintaining a strong impact force even at the end of the deep hole.

[0053] In this embodiment of the invention, the controller 5 establishes a precise correspondence between the pressure change of the high-pressure pump 1 and the movement of the piston 42, ensuring that the two pressure sources reach their respective peak states at the same time. This coordinated control strategy fully utilizes the energy of the two booster sources, avoids energy waste caused by phase misalignment, and significantly improves the effect of pulse boosting.

[0054] In some embodiments, the controller 5 includes a pressure detection unit for detecting the pressure pulsation frequency of the high-pressure pump 1.

[0055] In this invention, the controller 5 is equipped with a pressure detection unit to detect the pressure pulsation frequency of the high-pressure pump 1, providing accurate pressure feedback information to the system and realizing closed-loop control based on real-time pressure status. The pressure detection unit can accurately capture the changing pattern of the output pressure of the high-pressure pump 1, providing frequency and phase information to the controller 5 to ensure precise synchronization between the pulse boosting mechanism 4 and the high-pressure pump 1.

[0056] Specifically, the pressure detection unit is installed at an appropriate location at the output end of the high-pressure pump 1 or in the liquid supply line 2, and monitors the changes in liquid pressure in real time through a pressure sensor. The controller 5 receives the feedback signal from the pressure detection unit, analyzes the frequency characteristics of the pressure pulsation, and adjusts the operating parameters of the pulse boosting mechanism 4 accordingly to keep the two in a synchronized state.

[0057] Optionally, the controller 5 can also be equipped with a frequency synchronizer to ensure that the high-pressure pump 1 and the motor 45 can maintain a high degree of synchronization.

[0058] In some embodiments, the distance between the pulse boosting mechanism 4 and the nozzle 3 is less than 1 meter.

[0059] In this invention, the distance between the pulse boosting mechanism 4 and the nozzle 3 is limited to within 1 meter, effectively reducing the transmission loss of the high-pressure liquid in the pipeline after boosting, and ensuring that the pulse boosting effect can be effectively transmitted to the nozzle 3. When the high-pressure pulse jet is transmitted in the pipeline, pressure attenuation will occur due to frictional resistance. The longer the distance, the more obvious the attenuation, especially the peak pressure attenuation of the pulse jet is more severe.

[0060] Specifically, the high-pressure pulsed liquid generated by the pulse booster mechanism 4 is transmitted to the nozzle 3 through a short pipeline. The 1-meter distance limit ensures the flexibility of the equipment layout while keeping the pressure loss during transmission within a small range. The short transmission distance allows the pressure peak after boosting to be maintained more completely at the nozzle 3 outlet.

[0061] In one specific embodiment, when performing deep hole deburring, the nozzle 3 needs to extend into the workpiece. If the pulse boosting mechanism 4 is too far from the nozzle 3, the high-pressure pulse generated by the boosting will be significantly attenuated during transmission through the long pipeline, and the pressure peak will be significantly reduced by the time it reaches the nozzle 3. By controlling the distance to within 1 meter, it can be ensured that a sufficiently high pulse pressure can still be obtained at the nozzle 3.

[0062] In this embodiment of the invention, a clearly defined distance limit ensures the effective utilization of the pressurization effect. A distance of 1 meter satisfies the deployment requirements in practical applications while keeping transmission loss within an acceptable range, achieving a balance between pressurization effect and application convenience.

[0063] In some embodiments, the nozzle 3 is a ceramic nozzle 3.

[0064] In this invention, the nozzle 3 is manufactured using ceramic material, which fully utilizes the excellent wear resistance and high-pressure impact resistance of ceramic material, significantly improving the service life of the nozzle 3 under pulsed pressurized jet environment. The hardness of ceramic material is much higher than that of conventional metal materials, enabling it to withstand the impact of high-pressure pulsed jets for a long time while maintaining the accuracy of the nozzle orifice geometry.

[0065] Specifically, when subjected to periodic high-pressure pulse impacts, the high hardness and excellent fatigue resistance of the ceramic nozzle 3 ensure that the nozzle orifice will not experience significant wear or deformation due to long-term use. The chemical stability of the ceramic material also allows it to adapt to various working media without corrosion.

[0066] In one specific embodiment, when performing burr removal operations on a large batch of workpieces, the nozzle 3 needs to withstand high-intensity pulse jet impacts for extended periods. Traditional metal nozzles 3 are prone to problems such as orifice enlargement and edge wear under these conditions, affecting jet accuracy and pressure. The ceramic nozzle 3, however, can maintain stable jet characteristics over a long period under the same conditions.

[0067] In this embodiment of the invention, the ultra-high hardness and excellent impact resistance of the ceramic material enable the nozzle 3 to maintain stable performance over a long period of time in the harsh working environment of pulsed pressurized jets. The service life of the ceramic nozzle 3 significantly exceeds that of the metal nozzle 3, reducing maintenance costs and downtime.

[0068] like Figure 3 As shown, in some embodiments, the ceramic nozzle 3 includes a tube 31, one end of which is connected to the liquid supply line 2, and the other end of which is closed. Multiple sets of injection holes 32 are provided on the side wall of the tube 31, and the multiple sets of injection holes 32 are distributed at intervals along the axial direction of the tube 31.

[0069] In this invention, the ceramic nozzle 3 adopts a structure in which one end of the tube body 31 is open and the other end is closed, and multiple sets of axially spaced injection holes 32 are provided on the side wall of the tube body 31, achieving the effect of simultaneous jetting in multiple directions. The closed end of the tube body 31 forces the high-pressure liquid to flow out from the injection holes 32 on the side wall, and the axial distribution of multiple sets of injection holes 32 can simultaneously impact burrs at different locations.

[0070] Specifically, one end of the tube 31 is connected to the liquid supply line 2 to receive high-pressure pulsed liquid, while the other end is sealed to prevent the liquid from flowing out axially. The liquid is forced to spray out from the injection holes 32 on the side wall to form a radial jet. Multiple sets of injection holes 32 are distributed at intervals along the axial direction of the tube 31, so that the nozzle 3 can generate multiple jets simultaneously within a certain range in the axial direction, thus expanding the effective range of action.

[0071] In one specific embodiment, when cleaning a workpiece with a cross-hole structure, a conventional single-hole axial nozzle 3 requires multiple adjustments to its position to clean burrs in different directions. The multi-hole lateral spray design allows for simultaneous cleaning of multiple directions of the cross-holes in one operation, significantly improving work efficiency. The jet generated by each set of spray holes 32 can cover different areas of the hole wall.

[0072] In some embodiments, the axis of the injection hole 32 forms a 135° angle with the axis of the tube body 31.

[0073] In this invention, the axis of the injection orifice 32 forms a 135° angle with the axis of the tube body 31, achieving an optimized balance between jet impact force and coverage range. The 135° angle design ensures that the jet has sufficient radial component to impact the burrs on the orifice wall while maintaining an appropriate axial component to ensure the jet's penetration capability. Specifically, the 135° angle prevents the jet direction from being excessively radial or axial; the radial component ensures an effective frontal impact on the burrs on the orifice wall, while the axial component guarantees good penetration, allowing the jet to reach deep into the orifice. This angle design also facilitates backflow and debris removal after jet impact.

[0074] In one specific embodiment, when cleaning burrs from the inner wall of a deep hole, if the spray angle is too small, the jet mainly propagates axially, resulting in limited impact on radial burrs; if the angle is too large, the axial penetration capability of the jet is insufficient, making it difficult to reach the bottom of the deep hole. A 135° angle achieves a balance between depth and width cleaning, realizing a spiral cleaning trajectory.

[0075] In this embodiment of the invention, the 135° included angle is optimized through hydrodynamics, which can reduce energy loss after the jet collides with the orifice wall while ensuring impact force. This angle design also facilitates the discharge of burrs and debris generated during cleaning with the jet, avoiding secondary pollution and improving the thoroughness of cleaning.

[0076] In some embodiments, the spray holes 32 are provided in three groups, with each group of spray holes 32 having two spray holes 32.

[0077] In this invention, the injection holes 32 are configured in three groups, with each group containing two injection holes 32, achieving an optimized balance between cleaning efficiency, structural strength, and manufacturing cost. The axial distribution of the three groups can cover a longer cleaning range, and the arrangement of two holes in each group ensures sufficient jet density while avoiding the weakening of the tube body 31 due to excessive holes.

[0078] Specifically, the spacing of the three sets of injection holes 32 along the axial direction of the pipe body 31 can adapt to the cleaning needs of channels of various lengths. The two injection holes 32 in each set form a symmetrical distribution to generate a balanced radial jet force. The configuration of a total of 6 injection holes 32 controls the processing difficulty and cost while ensuring the cleaning effect.

[0079] This invention provides a burr removal method using the aforementioned high-pressure jet system, comprising the following steps: Start high-pressure pump 1 to generate high-pressure liquid with pressure pulsation; The controller 5 controls the movement frequency of the pulse booster mechanism 4 to synchronize with the pressure pulsation frequency of the high-pressure pump 1.

[0080] In this invention, a pulsed jet burr removal method is achieved by activating a high-pressure pump 1 to generate a high-pressure liquid with pressure pulsation, and by controlling the movement frequency of the pulse boosting mechanism 4 to synchronize with the pressure pulsation frequency of the high-pressure pump 1 through a controller 5. This method transforms the aforementioned device technology into a specific operational procedure, providing methodological guidance for the practical application of pulsed jet technology.

[0081] Specifically, the high-pressure pump 1 is started to establish the basic pressure source of the system. The working characteristics of the high-pressure pump 1 will generate certain pressure pulsations. The controller 5 detects the frequency characteristics of these pressure pulsations and adjusts the motion parameters of the pulse boosting mechanism 4 accordingly to synchronize its motion frequency with the pressure pulsation frequency, thereby producing a coordinated pulse boosting effect.

[0082] In one specific embodiment, when performing deburring operations on batches of parts, after the operator starts the equipment according to this method, the system can automatically maintain the optimal pulse boost state for continuous operation. Compared with the traditional method that requires manual adjustment of jet parameters, this method achieves automated parameter matching, improving the consistency and efficiency of the operation.

[0083] In this embodiment of the invention, the pulsed jet method generates high-voltage pulses through frequency synchronization matching, which can strongly impact burrs in a short time, rapidly removing burrs by utilizing the destructive effect of instantaneous high pressure. This method is particularly suitable for the efficient removal of hard burrs, significantly shortening the removal time and reducing energy consumption compared to the continuous jet method.

[0084] In some embodiments, as the output pressure of the high-pressure pump 1 increases, the pressure of the pulse booster mechanism 4 increases synchronously; as the output pressure of the high-pressure pump 1 decreases, the pressure of the pulse booster mechanism 4 decreases synchronously.

[0085] In this invention, optimal coordination between the two pressure boosting sources is achieved through coordinated control of the pulse boosting mechanism 4 synchronously boosting pressure during the increase of output pressure from the high-pressure pump 1 and synchronously reducing pressure during the decrease of output pressure. This synchronous boosting and depressurization control strategy ensures the in-phase nature of pressure changes and avoids mutual cancellation caused by out-of-phase operation.

[0086] Specifically, when the output pressure of high-pressure pump 1 is in the rising phase, the pulse boosting mechanism 4 simultaneously performs boosting action, and the boosting effect of the two pressure sources is superimposed to produce a higher peak pressure. When the output pressure of high-pressure pump 1 is in the decreasing phase, the pulse boosting mechanism 4 correspondingly reduces the boosting amplitude or stops boosting to avoid generating an excessive pressure difference in the low-pressure phase of high-pressure pump 1.

[0087] In this embodiment of the invention, the coordinated control of synchronous pressurization and synchronous depressurization fully leverages the synergistic effect of the two pressurization sources. Synchronous control enables the system to generate stable and reliable high-pressure pulses, providing an effective technical means for burr removal tasks of various difficulties and significantly enhancing the practical value of pulsed pressurized jets.

[0088] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs. Those skilled in the art can understand and implement this without any creative effort.

[0089] 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 high-pressure jet system, characterized in that, include: High-pressure pump (1); Liquid supply line (2), one end of which is connected to the output end of the high pressure pump (1); The nozzle (3) is connected to the end of the liquid supply line (2) away from the high-pressure pump (1); A pulse boosting mechanism (4) is provided on the liquid supply pipeline (2); The controller (5) is electrically connected to the high-pressure pump (1) and the pulse boosting mechanism (4) respectively, and is used to control the movement frequency of the pulse boosting mechanism (4) to match the pressure pulsation frequency of the high-pressure pump (1) so that the medium sprayed by the nozzle (3) is in a pulse boosting state.

2. The high-pressure jet system according to claim 1, characterized in that, The pulse boosting mechanism (4) includes: The housing (41) has a cavity (411) and the housing (41) is connected to the liquid supply line (2); The piston (42) is slidably disposed in the cavity (411), and the piston (42) can reciprocate along the cavity (411) to change the volume of the cavity (411); A drive assembly, the output end of which is connected to the piston (42) for driving the piston (42) to reciprocate; The first check valve (43) is installed on the liquid supply line (2) and located at the inlet (412) of the housing (41).

3. The high-pressure jet system according to claim 2, characterized in that, The pulse boosting mechanism (4) further includes a second one-way valve (44), which is disposed in the liquid supply pipeline (2) and located at the output port (413) of the housing (41).

4. The high-pressure jet system according to claim 2, characterized in that, The piston (42) is provided with a transmission hole (421), and the drive assembly includes: Motor (45); A cam (46) is provided at the output end of the motor (45) and is provided in the transmission hole (421) to drive the piston (42) to reciprocate. The operating frequency of the motor (45) is matched with the frequency of the high-pressure pump (1).

5. The high-pressure jet system according to claim 2, characterized in that, The controller (5) is configured to: control the output pressure of the high-pressure pump (1) to be in the rising stage during the process of the volume reduction of the cavity (411); and control the output pressure of the high-pressure pump (1) to be in the falling stage during the process of the volume increase of the cavity (411).

6. The high-pressure jet system according to any one of claims 1-5, characterized in that, The distance between the pulse boosting mechanism (4) and the nozzle (3) is less than 1 meter.

7. The high-pressure jet system according to any one of claims 1-5, characterized in that, The nozzle (3) is a ceramic nozzle (3).

8. The high-pressure jet system according to any one of claims 1-5, characterized in that, The nozzle (3) includes a tube (31), one end of which is connected to the liquid supply line (2), and the other end of which is closed. Multiple sets of injection holes (32) are provided on the side wall of the tube (31), and the multiple sets of injection holes (32) are distributed at intervals along the axial direction of the tube (31).

9. The high-pressure jet system according to claim 8, characterized in that, The axis of the injection hole (32) forms a 135° angle with the axis of the tube body (31).

10. The high-pressure jet system according to claim 8, characterized in that, The spray holes (32) are provided in three groups, and each group of spray holes (32) is provided with two spray holes (32).

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