A die casting liquid supply stabilization mechanism

Abstract

This application relates to the field of die casting equipment technology, and provides a die casting liquid supply component stabilization mechanism, including a connecting pipe connected to the end of the liquid supply arm, a movable block axially sliding in the connecting pipe, and a guide groove hinged to the inner side of the movable block; a limiting dome located above the guide groove is provided on the connecting pipe, and a jet port with variable cross-sectional area is formed between the bottom side of the limiting dome and the top side of the guide groove; this application also includes a first compensation component driven by static pressure to cause the movable block to produce a retraction displacement, and a second compensation component driven by dynamic pressure to cause the guide groove to deflect and the supporting fulcrum to move forward in linkage; this application achieves adaptive adjustment of the cross-sectional area of ​​the jet port and the injection elevation angle by decoupling the changes of fluid static pressure and dynamic pressure and converting them into superimposed coupling of mechanical displacement, so that the parabolic landing point of the cast liquid is kept in the preset landing point area corresponding to the center of the target pressure chamber under the condition of flow velocity fluctuation, thus solving the problems of liquid injection splashing, air entrapment and cold shut scrap.

Description

Technical Field

[0001] This application relates to the field of die casting equipment technology, specifically to a die casting liquid supply stabilization mechanism. Background Technology

[0002] In the alloy die casting process, the "airborne stage"—the phase where molten metal flies from the supply arm (such as the injection nozzle) to the pressure chamber (injection hole) of the die casting machine—is a critical factor affecting casting quality. Due to gravity and initial momentum, the molten metal travels in a parabolic trajectory through the air. Ideally, the molten metal should fall precisely into the depths of the pressure chamber to minimize air entrapment and splashing.

[0003] However, in actual production, no matter how precise the metering pump or tilting mechanism is, the flow velocity of the molten metal leaving the nozzle inevitably undergoes a dynamic change process of "small (initial) - large (mid-term) - small (final)" due to fluctuations in the supply pressure, changes in the liquid level, and pipe resistance. Since the parabolic trajectory is highly dependent on the initial flow velocity, fluctuations in velocity cause severe "drift" in the trajectory of the ejected liquid flow. At the beginning and end of the supply phase, the insufficient kinetic energy of the liquid flow often prevents it from entering the center of the pressure chamber, instead impacting the sidewall of the pressure chamber or the edge of the injection hole, instantly causing splashing and entraining a large amount of air. Even more seriously, the molten metal impacting the sidewall cools rapidly, forming an oxide scale (cold shut), which is then pushed into the mold by the main injection head, directly leading to the scrapping of the casting.

[0004] Existing technologies attempt to use electronic sensors (such as ultrasonic or infrared flow meters) in conjunction with servo mechanisms to adjust the nozzle angle in real time. However, the die-casting site is an environment of extreme high temperature, strong vibration and heavy dust, and the sensing elements are prone to failure or signal drift; at the same time, because the molten metal is prone to condensation at the gaps between the moving parts, conventional dynamic adjustment mechanisms are prone to jamming or leakage.

[0005] Therefore, there is an urgent need in the existing technology for a die-casting liquid supply stabilization mechanism, which aims to automatically sense the fluctuations in fluid pressure (including static and dynamic pressure) in the liquid guiding chamber without relying on external electronic sensor triggering, and use the pressure change to drive mechanical components to generate precise displacement compensation, so as to adjust the cross-sectional area of ​​the jet orifice and the launch angle of the jet, thereby keeping the landing point of the ejected metal liquid parabola within the preset landing point area corresponding to the center of the target pressure chamber under full liquid supply conditions, and simultaneously solving the dynamic sealing and leakage prevention problem in the high-temperature liquid metal environment. Summary of the Invention

[0006] This application discloses a die-casting liquid supply component stabilization mechanism. By providing axial displacement feedback of the movable block to respond to the static pressure change of the molten casting in the liquid guiding cavity, performing tilt angle deflection and displacement coupling of the support fulcrum to respond to the dynamic pressure flowing through the guide channel, and adjusting the cross-sectional area of ​​the jet outlet between the limiting dome and the guide channel, a closed-loop processing chain is formed that responds to flow velocity fluctuations and compensates for the jet elevation angle and cross-sectional area. This ensures that the parabolic landing point of the ejected molten casting remains within the preset landing point area corresponding to the center of the target pressure chamber, eliminating trajectory drift, splashing, and air entrapment caused by flow velocity attenuation, and improving the stability and reliability of the die-casting liquid supply process.

[0007] To achieve the above objectives, the technical solution of this application is as follows: a die-casting liquid supply component stabilization mechanism includes a connecting pipe connected to the end of a liquid supply arm, a movable block axially movable in the connecting pipe, a guide groove rotatably disposed on the inner side of the movable block and synchronized with its axial movement, and a guide cavity for conveying the casting liquid in the liquid supply arm to the inlet end of the guide groove in the connecting pipe; a limiting dome located above the outlet end of the guide groove is provided at the end of the connecting pipe away from the liquid supply arm, and a jet port with variable cross-sectional area is formed between the bottom side of the limiting dome and the top side of the outlet end of the guide groove;

[0008] The die-casting liquid supply stabilization mechanism further includes a first compensation component and a second compensation component; the first compensation component responds to the static pressure of the casting liquid in the liquid guiding cavity and can adjust the relative position of the guide channel and the limiting dome in the axial direction of the connecting pipe; the second compensation component responds to the dynamic fluid pressure generated when the casting liquid flows through the guide channel and superimposes and couples the axial relative position change generated by the first compensation component, and can adapt to adjust the cross-sectional area and ejection angle of the jet nozzle so that the landing point of the ejection parabola of the casting liquid is kept within the preset landing point area corresponding to the center of the target pressure chamber.

[0009] It should be noted that, in this application, the target pressure chamber center refers to the central area formed by the intersection of the center line of the pressure chamber injection hole and the predetermined falling section of the molten casting; the preset landing point area corresponding to the target pressure chamber center is the allowable landing point range formed around the central area, and the allowable landing point range is determined based on the diameter of the pressure chamber injection hole, the installation distance between the liquid outlet end of the guide channel and the pressure chamber injection hole, and the allowable splash boundary of the molten casting.

[0010] This scheme achieves passive coupling between fluid dynamics signals and pure mechanical displacement, utilizing the energy of the molten casting itself to adjust the jetting attitude, reducing parabolic trajectory drift and air entrapment upon impact with the wall.

[0011] Furthermore, a pressure-guiding hole is radially formed in the connecting pipe, communicating with the liquid guiding cavity; the first compensation component includes a hydrostatic transmission component, the input end of which is connected to the liquid guiding cavity through the pressure-guiding hole to sense the static pressure of the casting liquid, and the output end of which is connected to the movable block for transmission, used to convert the static pressure of the casting liquid into a thrust that drives the movable block to undergo axial retraction displacement in the direction of the liquid supply arm. A macroscopic hydrostatic pressure signal is extracted through the pressure-guiding hole, establishing a first-level pressure feedback reference.

[0012] Furthermore, the hydrostatic transmission assembly includes a fixed plate fixedly disposed in the pressure guiding hole, a push rod elastically inserted into the fixed plate that can move relative to it, a pressure plate for hydrostatic driving of the casting liquid in the liquid guiding cavity being disposed at one end of the push rod near the liquid guiding cavity, and a transmission rod axially slidably inserted inside the connecting pipe; one end of the transmission rod is fixedly connected to a movable block near the liquid supply arm, and a slanted groove is formed on the outer wall of the transmission rod near the other end, with the other end of the push rod slidingly pressing against the slanted groove. The radial pressure is converted into axial displacement through the wedge transmission, achieving smooth conversion of the signal dimension and mechanical amplification.

[0013] Furthermore, a groove parallel to the moving direction is formed on the inner bottom wall of the movable block, and the second compensation component includes a slider slidably disposed in the groove; the liquid inlet end of the guide channel is hinged to the inner side of the movable block via a rotating shaft, and the bottom side of the guide channel is supported on the slider; when the guide channel is deflected by the dynamic fluid pressure of the casting liquid and exerts a squeezing effect on the slider through its bottom side, the slider slides relative to the movable block within the groove to change the support fulcrum position of the guide channel. By establishing the relative motion relationship between the movable block and the slider, a spatial basis is provided for subsequent differential coupling.

[0014] Furthermore, a track groove is formed on the bottom side of the guide channel, and a track wheel is rotatably mounted above the slider. The track wheel is confined within the track groove to support the guide channel. When the guide channel is deflected downward by the dynamic fluid pressure of the casting liquid, the track groove presses down on the track wheel and generates a horizontal component force, driving the slider to slide away from the supply arm within the trough. By inducing track extrusion through dynamic pressure, stiffness adjustment is achieved by "the faster the flow rate, the further forward the fulcrum moves".

[0015] Furthermore, a vertical cylinder is fixed to the top of the slider, and a vertical rod is slidably inserted into the top side of the vertical cylinder. A wheel seat is provided at the top of the vertical rod, and the track wheel is rotatably mounted on the wheel seat via an axle. A washer is sleeved and fixed to the outside of the vertical rod, and a first spring is sleeved on the outside of the vertical rod, with the two ends of the first spring abutting against the bottom side of the washer and the top side of the vertical cylinder, respectively. When the guide channel deflects downward, the first spring is compressed and deformed. When the dynamic fluid pressure of the casting liquid acting on the guide channel decreases, causing the downward pressure exerted by the track channel on the track wheel to be less than the reset support force exerted by the first spring through the vertical rod, the first spring pushes the vertical rod upward and drives the guide channel to reset upward.

[0016] Furthermore, a second spring is sleeved on the outer side of the push rod, and the two ends of the second spring are respectively connected to the corresponding side walls of the fixed plate and the corresponding side walls of the pressure plate; when the pressure plate is driven by the pressure of the casting liquid fluid to move towards the fixed plate, the second spring is compressed and deformed. The preload of the second spring is determined based on the pressure area of ​​the pressure plate, the working pressure range of the liquid guiding cavity, and the required axial retraction starting position of the movable block; when the thrust generated by the static pressure of the casting liquid acting on the pressure plate exceeds the preload reset force of the second spring, the push rod begins to move towards the fixed plate.

[0017] Furthermore, the movable block has a second movable cavity inside, and the guide channel is located within the second movable cavity. Connecting arms are respectively provided on both sides of the guide channel along its width direction. The liquid inlet end of the guide channel is connected to the rotating shaft through the connecting arms. The end face of the liquid inlet end of the guide channel is a convex arc surface, and the inner wall of the second movable cavity has a concave arc surface corresponding to the convex arc surface. Both the convex and concave arc surfaces are coaxially arranged with the rotating shaft as the center. By utilizing the geometric fit between the eccentric rotating shaft and the coaxial arc surface, a stable narrow-slit seal is established at the dynamic-static interface, effectively preventing side leakage of molten aluminum due to gravity and pressure.

[0018] Furthermore, the movable block has a conduit connecting the liquid guiding cavity and the flow guiding channel at one end facing the liquid supply arm. A third spring is sleeved on the outside of the conduit, and the two ends of the third spring abut against the inner wall of the connecting pipe and the side wall of the movable block, respectively. When the movable block moves towards the liquid supply arm, the third spring is compressed and deformed. The third spring ensures that the movable block can quickly pop forward at the moment the liquid supply ends, assisting the flow guiding channel in completing the physical cutoff of the residual liquid at the end.

[0019] Furthermore, the liquid guiding cavity includes a first flow channel, a second flow channel, and a third flow channel sequentially connected within a connecting pipe along the casting liquid conveying direction; the guide tube slidably passes through the third flow channel, and a piston ring is provided on the outer wall of the guide tube, the piston ring being in a sealing sliding fit with the inner wall of the third flow channel. The high-temperature dynamic sealing environment constructed by the piston ring ensures that leakage from the liquid guiding cavity is avoided during large-scale reciprocating movement of the moving block.

[0020] The beneficial effects of this application are reflected in:

[0021] This application establishes a fluid dynamics feedback processing chain that is executed sequentially along the order of "pressure capture, displacement transmission, fulcrum forward movement, and landing point locking" by the first compensation component for axial transmission of static pressure and the second compensation component for attitude transformation of dynamic pressure, so that the parabolic trajectory of the ejected liquid flow is always adjusted by the negative feedback of the fluid's own kinetic energy state.

[0022] Firstly, in this application, the relative motion between the guide channel and the limiting dome is used to change the shape of the jet orifice, and the superimposed coupling effect of the first and second compensation components is used to convert the fluid pressure fluctuation into self-compensation of the ejection elevation angle and cross-sectional area. Therefore, the parabolic landing point of the molten metal can be kept within the preset landing point area corresponding to the center of the target pressure chamber during the dynamic change of the flow velocity. This solves the problems of air entrapment, splashing and cold shut-off caused by the landing point drift and hitting the edge of the pressure chamber in traditional liquid supply devices.

[0023] Secondly, in this application, the first compensation component is used to convert the static pressure of the casting liquid in the liquid guiding cavity into the axial retraction displacement of the movable block. This is beneficial to buffer the instantaneous impact of the liquid flow by driving the movable block to generate axial retraction displacement in the direction of the liquid supply arm during the middle of a large flow liquid supply, stabilize the flow field, and improve the stability of the mechanism under high pressure conditions.

[0024] Thirdly, in this application, the second compensation component utilizes the compression of the track wheel by the guide channel under dynamic pressure to achieve the relative forward movement of the slider, which dynamically shortens the support arm. This is beneficial to increase the mechanical support stiffness of the mechanism by automatically moving the fulcrum forward during the stage of fastest flow velocity and strongest kinetic energy, thus eliminating the influence of jet vibration on the landing point accuracy.

[0025] Fourth, in this application, the coaxial clearance fit between the convex arc surface and the concave arc surface restricts the outward circumferential leakage of the casting liquid along the inlet end of the guide channel, and the surface tension of the molten metal reduces the possibility of the casting liquid continuing to seep out through the gap, which is conducive to maintaining a long-term dynamic anti-leakage effect in the high-temperature liquid metal environment and solves the problem of easy jamming and leakage of moving parts.

[0026] Fifth, this application utilizes the fluid's own pressure as a power source to drive a purely mechanical transmission chain, without relying on electronic sensors and external triggering sources that are susceptible to high temperatures and vibrations. Therefore, even in the harsh environment of the die-casting site, it is still beneficial to maintain the synchronization of actions and the reliability of execution. Attached Figure Description

[0027] In the attached diagram:

[0028] Figure 1 This is a three-dimensional structural diagram of the entire application at the initial or final stage of liquid supply.

[0029] Figure 2 for Figure 1 A cross-sectional structural diagram of the device;

[0030] Figure 3 This is a three-dimensional structural diagram of the entire application when it is in the middle stage of liquid supply;

[0031] Figure 4 for Figure 3 A cross-sectional structural diagram of the device;

[0032] Figure 5 for Figure 4 Enlarged structural diagram at point A;

[0033] Figure 6 for Figure 4 Enlarged structural diagram at point B;

[0034] Figure 7 for Figure 2 A schematic cross-sectional view of the moving block and the conduit.

[0035] Figure 8 for Figure 2 Structural diagram of the slider, vertical cylinder, vertical rod, and track wheels, etc.;

[0036] Figure 9 for Figure 2 A top view of the central guide channel;

[0037] Figure 10 for Figure 2 A schematic diagram of the structure of the central guide channel from below.

[0038] Explanation of reference numerals in the attached figures:

[0039] 1. Connecting pipe; 2. Connecting port; 3. First movable cavity; 4. First flow channel; 5. Second flow channel; 6. Third flow channel; 7. Movable block; 8. Guide tube; 9. Second movable cavity; 10. Concave arc surface; 11. Guide groove; 12. Convex arc surface; 13. Connecting arm; 14. Rotating shaft; 15. Piston ring; 16. Movable port; 17. Sliding block; 18. Slide groove; 19. Vertical cylinder; 20. Vertical rod; 21. Washer ring; 22. Track groove; 23. Track wheel; 24. Pressure guide hole; 25. Fixed plate; 26. Pressure plate; 27. Top rod; 28. Transmission rod; 29. ​​Inclined groove; 30. Limiting dome; 31. Jet port. Detailed Implementation

[0040] The present application will now be described in further detail with reference to the accompanying drawings and embodiments. Obviously, the described embodiments are merely some, not all, of the embodiments of the present application. Unless otherwise specified, the embodiments and features described in the present application can be combined with each other. All other embodiments obtained by those skilled in the art based on the embodiments of the application without inventive effort are within the scope of protection of the application.

[0041] Please combine Figures 1 to 10 The die-casting liquid supply stabilization mechanism includes a connecting pipe 1 connected to the end of the liquid supply arm, which serves as the load-bearing foundation for the entire mechanism. The connecting pipe 1 has a connecting port 2, which is used for a sealed connection with the quantitative liquid supply mechanism or the end of the liquid supply arm, so that the first flow channel 4 receives the casting liquid output by the quantitative liquid supply mechanism.

[0042] The connecting pipe 1 has a first movable cavity 3 inside, and a movable block 7 is axially movable inside the first movable cavity 3. A guide groove 11 is rotatably provided inside the movable block 7, which is synchronized with its axial movement. That is, the movable block 7 has a second movable cavity 9 inside, and the guide groove 11 is hinged to the second movable cavity 9 through a rotating shaft 14. In order not to interfere with the up and down deflection of the guide groove 11, the first movable cavity 3 has a movable opening 16 at the position corresponding to the deflection path of the guide groove 11.

[0043] The connecting pipe 1 has a liquid guiding cavity for conveying the casting liquid in the supply arm to the liquid inlet end of the guide channel 11; the end of the connecting pipe 1 away from the supply arm is provided with a limiting dome 30 located above the liquid outlet end of the guide channel 11. The bottom side of the limiting dome 30 forms an arc-shaped limiting surface extending along the casting liquid ejection direction. The arc-shaped limiting surface and the top side of the liquid outlet end of the guide channel 11 together define the jet port 31 (the gap formed between the arc-shaped limiting surface and the liquid outlet end of the guide channel 11 constitutes the jet port 31 with a variable cross-sectional area). That is, when the movable block 7 drives the guide channel 11 to undergo axial displacement, or when the guide channel 11 deflects around the rotating shaft 14, the cross-sectional area of ​​the jet port 31 and the take-off angle relative to the horizontal plane change accordingly.

[0044] Regarding the liquid guiding path, the connecting pipe 1 has a first flow channel 4, a second flow channel 5, and a third flow channel 6 sequentially connected along the direction of casting liquid delivery, which together form a liquid guiding cavity. A conduit 8 is fixedly connected to the end of the movable block 7 facing the liquid supply arm. The conduit 8 is slidably inserted into the third flow channel 6 through a piston ring 15 fitted on its outer side. This "piston-conduit" structure ensures that the casting liquid can be smoothly introduced from the third flow channel 6 into the inlet end of the guide groove 11 throughout the entire stroke of the movable block 7's displacement. The piston ring 15 can be a high-temperature resistant graphite ring, a ceramic sealing ring, or a high-temperature alloy sealing ring, and the outer circumferential surface of the piston ring 15 forms a sliding seal with the inner wall of the third flow channel 6.

[0045] The device also includes a first compensation component and a second compensation component;

[0046] In one embodiment, the first compensation component serving as the hydrostatic transmission path includes a pressure guiding hole 24 formed in the wall of the connecting pipe 1 and communicating with the first flow channel 4. A fixed plate 25 is fixed inside the pressure guiding hole 24, and a push rod 27 is elastically inserted into the fixed plate 25. A pressure bearing plate 26 is provided at one end of the push rod 27 near the flow channel for directly sensing the hydrostatic pressure of the fluid. A second spring is sleeved on the outside of the push rod 27, and the two ends of the second spring are respectively connected to the fixed plate 25 and the pressure bearing plate 26. A transmission rod 28 is also slidably inserted into the connecting pipe 1. One end of the transmission rod 28 is fixed to the rear end of the movable block 7, and the other end extends above the push rod 27 and has an inclined groove 29. The ball end of the push rod 27 is inserted into the inclined groove 29 and slides and presses against it.

[0047] In this embodiment, the inclined groove 29 extends axially along the transmission rod 28 and is inclined relative to the axis of the transmission rod 28; when the push rod 27 moves away from the liquid guiding cavity under the drive of the pressure plate 26, the end of the push rod 27 slides along the inclined groove wall of the inclined groove 29 and applies an axial component force to the transmission rod 28, so that the transmission rod 28 drives the movable block 7 to move towards the liquid supply arm.

[0048] In one embodiment, the second compensation component serving as the dynamic pressure transmission path includes a groove 18 formed on the inner bottom wall of the movable block 7, with a slider 17 slidably disposed within the groove 18. A vertical cylinder 19 is fixed to the top of the slider 17, and a vertical rod 20 is slidably inserted into the vertical cylinder 19. A wheel seat is provided at the top of the vertical rod 20, and a track wheel 23 is rotatably mounted on the wheel seat via an axle. A washer ring 21 is sleeved on the outer side of the vertical rod 20, and a first spring is sleeved on the outer side of the vertical rod 20, with the first spring abutting between the washer ring 21 and the top side of the vertical cylinder 19. A track groove 22 is formed on the bottom side of the guide channel 11, and the track wheel 23 is confined within the track groove 22 to support the guide channel 11. Connecting arms 13 are vertically provided on both sides of the guide channel 11, and are mounted on the rotating shaft 14 via the connecting arms 13.

[0049] In this embodiment, the bottom of the track groove 22 has a guide surface that gradually rises or falls along the liquid outlet direction of the guide groove 11, and the track wheel 23 rolls in contact with the guide surface. When the guide groove 11 deflects downward, the guide surface applies a component force along the length direction of the slide 18 to the track wheel 23, causing the slider 17 to slide away from the liquid supply arm. When the guide groove 11 deflects downward, the track groove 22 presses the upright 20 down relative to the vertical cylinder 19 through the track wheel 23, and the washer ring 21 compresses the first spring. When the dynamic fluid pressure decreases, the first spring pushes the upright 20 up, and the upright 20 pushes the track groove 22 through the track wheel 23, causing the guide groove 11 to return to its original position around the rotating shaft 14.

[0050] To prevent side leakage at the rotating shaft due to pressure fluctuations, the inlet end of the guide channel 11 is provided with a convex arc surface 12 and a concave arc surface 10 floating on the inner wall of the second movable cavity 9. Both are coaxially arranged with the rotating shaft 14 as the center. Specifically, the convex arc surface 12 at the inlet end of the guide channel 11 and the concave arc surface 10 on the inner wall of the second movable cavity 9 are coaxially clearance-fitted. This clearance is determined based on the surface tension of the casting liquid, the allowable penetration distance of the casting liquid, and the deflection stroke of the guide channel 11, so that the inlet end of the guide channel 11 maintains liquid-blocking fit during the deflection process and avoids rotation jamming.

[0051] In addition, a third spring is fitted on the outside of the conduit 8. The third spring abuts between the inner wall of the connecting tube 1 and the side wall of the movable block 7 to provide overall reset force.

[0052] The working principle and linkage process of this application are as follows:

[0053] During the initial and final stages of liquid supply (low-speed phase), the flow rate of the molten casting is relatively slow. The static pressure is insufficient to fully lift the pressure plate 26, and the dynamic pressure is also insufficient to significantly depress the guide channel 11. At this time, the movable block 7 is positioned forward under the action of the third spring, and the guide channel 11 is in a relatively upward tilted position under the action of the first spring, causing the cross-sectional area of ​​the jet nozzle 31 to shrink. After the cross-sectional area of ​​the jet nozzle 31 decreases, the ejection velocity of the molten casting through the jet nozzle 31 increases with the same liquid supply. The upward tilted position of the guide channel 11 also increases the ejection angle, thereby compensating for the landing point deviation caused by gravity in the low-speed phase, and ensuring that the liquid flow accurately falls into the pressure chamber.

[0054] During the middle stage of liquid supply (high flow rate stage), the flow rate surges. On one hand, the static pressure of the molten liquid in the first flow channel 4 pushes the pressure plate 26 to move along the pressure guide hole 24 towards the fixed plate 25. The pressure plate 26 drives the push rod 27 to compress the second spring and squeeze the inclined groove 29. Through the inclined wedge transmission, the transmission rod 28 is forced to drive the movable block 7 to move backward (towards the liquid supply arm), resulting in an axial displacement of the movable block 7 towards the liquid supply arm. On the other hand, the high-speed liquid flow impacts and flows through the guide groove 11. The dynamic fluid pressure compresses the guide groove 11 to overcome the resistance of the first spring and deflect downward. The track groove 22 then sinks and squeezes the track wheel 23, generating a horizontal component force to drive the slider 17 to slide forward (away from the liquid supply arm) within the slide groove 18. During this process, the movable block 7 moves towards the liquid supply arm, and the slider 17 slides relative to the movable block 7 away from the liquid supply arm, causing the contact position between the track wheel 23 and the track groove 22 to move along the liquid outlet end of the guide groove 11, thereby shortening the lever arm between the liquid outlet end of the guide groove 11 and the support position. This "opposite movement" causes the fulcrum position of the support guide groove 11 to move forward sharply, improving the mechanical rigidity of the guide groove when subjected to large flow impact.

[0055] At the moment the liquid supply is cut off, the first spring, the second spring and the third spring release the reset force, the movable block 7 resets in the direction away from the liquid supply arm, and the guide groove 11 resets upward around the rotating shaft 14, so that the cross-sectional area of ​​the jet port 31 is reduced to the state of residual liquid cut-off, thereby reducing the tail material stringing and cold shut defects caused by the continued stretching and dripping of the end liquid column.

[0056] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

[0057] It should be noted that if the embodiments of the application involve directional indicators (such as up and down), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0058] Furthermore, the meaning of "and / or" throughout the text includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or a solution that simultaneously satisfies A and B. Additionally, if the embodiments of the application involve descriptions such as "first," "second," etc., these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, features defined with "first" or "second" can explicitly or implicitly include at least one of those features. Furthermore, "multiple" refers to two or more. Additionally, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of a person skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed in the application.

Claims

1. A die-casting liquid supply stabilization mechanism, characterized in that, The device includes a connecting pipe (1) connected to the end of the liquid supply arm. A movable block (7) is axially movable in the connecting pipe (1). A guide groove (11) is rotatably provided on the inner side of the movable block (7) and moves synchronously with it. The connecting pipe (1) has a guide cavity for conveying the casting liquid in the liquid supply arm to the liquid inlet end of the guide groove (11). A limiting dome (30) is provided at the end of the connecting pipe (1) away from the liquid supply arm, located above the liquid outlet end of the guide groove (11). A jet port (31) with a variable cross-sectional area is formed between the bottom side of the limiting dome (30) and the top side of the liquid outlet end of the guide groove (11). The die-casting liquid supply stabilization mechanism also includes a first compensation component and a second compensation component. The first compensation component responds to the static pressure of the casting liquid in the liquid guiding cavity and drives the movable block (7) to move the guide channel (11) axially along the connecting pipe (1) to change the axial position of the liquid outlet end of the guide channel (11) relative to the limiting dome (30). The second compensation component responds to the dynamic fluid pressure generated when the casting liquid flows through the guide channel (11), and is superimposed on the axial relative position change generated by the first compensation component; Based on the position of the guide channel (11) formed after the axial movement of the movable block (7), the second compensation component responds to the dynamic fluid pressure of the casting liquid acting on the guide channel (11) and changes the deflection angle and support position of the guide channel (11); By adjusting the cross-sectional area and ejection angle of the jet nozzle (31) through the axial movement of the movable block (7), the deflection of the guide channel (11), and the change in the position of the bottom support fulcrum of the guide channel (11), the ejection parabola landing point of the casting liquid is kept within the preset landing point area corresponding to the center of the target pressure chamber.

2. The die-casting liquid supply stabilization mechanism as described in claim 1, characterized in that, The connecting pipe (1) is radially provided with a pressure guiding hole (24) that communicates with the liquid guiding cavity; the first compensation component includes a static pressure transmission component, the input end of the static pressure transmission component is connected to the liquid guiding cavity through the pressure guiding hole (24) to sense the static pressure of the casting liquid, and the output end of the static pressure transmission component is connected to the movable block (7) for transmitting the static pressure of the casting liquid into a thrust that drives the movable block (7) to make an axial retraction displacement in the direction of the liquid supply arm.

3. The die-casting liquid supply stabilization mechanism as described in claim 2, characterized in that, The hydrostatic transmission assembly includes a fixed plate (25) fixedly installed in the pressure guiding hole (24), a push rod (27) that can move relative to the fixed plate (25) is elastically inserted on the fixed plate (25), a pressure plate (26) for driving the casting liquid in the liquid guiding cavity is provided at one end of the push rod (27) near the liquid guiding cavity, and a transmission rod (28) is axially slidably inserted in the connecting pipe (1); one end of the transmission rod (28) is fixedly connected to the movable block (7) near the side of the liquid supply arm, and a groove (29) is opened on the outer wall of the transmission rod (28) near the other end, and the other end of the push rod (27) is slidably squeezed into the groove (29).

4. The die-casting liquid supply stabilization mechanism as described in claim 1, characterized in that, The movable block (7) has a groove (18) parallel to its moving direction on its inner bottom wall. The second compensation component includes a slider (17) slidably disposed in the groove (18). The liquid inlet end of the guide channel (11) is hinged to the inner side of the movable block (7) through a rotating shaft (14). The bottom side of the guide channel (11) is supported on the slider (17). When the guide channel (11) is deflected by the dynamic fluid pressure of the casting liquid and squeezed by its bottom side onto the slider (17), the slider (17) slides relative to the movable block (7) in the groove (18) to change the support position of the guide channel (11).

5. The die-casting liquid supply stabilization mechanism as described in claim 4, characterized in that, The bottom side of the guide channel (11) is provided with a track groove (22), and a track wheel (23) is rotatably provided above the slider (17). The track wheel (23) is limited to the track groove (22) to support the guide channel (11). When the guide channel (11) is deflected downward by the dynamic fluid pressure of the casting liquid, the track groove (22) squeezes the track wheel (23) downward and generates a horizontal component force, driving the slider (17) to slide away from the liquid supply arm in the slide groove (18).

6. The die-casting liquid supply stabilization mechanism as described in claim 5, characterized in that, The top of the slider (17) is fixed with a vertical cylinder (19), and a vertical rod (20) is slidably inserted into the top side of the vertical cylinder (19). A wheel seat is provided at the top of the vertical rod (20), and the track wheel (23) is rotatably mounted on the wheel seat through the wheel axle. A washer (21) is sleeved and fixed on the outside of the vertical rod (20), and a first spring is sleeved on the outside of the vertical rod (20). The two ends of the first spring abut against the bottom side of the washer (21) and the top side of the vertical cylinder (19), respectively. When the guide groove (11) deflects downward, the first spring is compressed and deformed.

7. The die-casting liquid supply stabilization mechanism as described in claim 3, characterized in that, A second spring is sleeved on the outside of the top rod (27), and the two ends of the second spring are respectively connected to the corresponding side wall of the fixed plate (25) and the corresponding side wall of the pressure plate (26); when the pressure plate (26) is driven by the pressure of the casting liquid fluid to move towards the fixed plate (25), the second spring is compressed and deformed.

8. The die-casting liquid supply stabilization mechanism as described in claim 4, characterized in that, The movable block (7) has a second movable cavity (9) inside, and the guide groove (11) is located in the second movable cavity (9). The guide groove (11) is provided with connecting arms (13) on both sides along the width direction. The liquid inlet end of the guide groove (11) is connected to the rotating shaft (14) through the connecting arms (13). The end face of the liquid inlet end of the guide groove (11) is a convex arc surface (12). The inner wall of the second movable cavity (9) has a concave arc surface (10) corresponding to the convex arc surface (12). The convex arc surface (12) and the concave arc surface (10) are both coaxially arranged with the rotating shaft (14) as the center.

9. The die-casting liquid supply stabilization mechanism as described in claim 1, characterized in that, The movable block (7) is provided with a conduit (8) connecting the liquid guiding cavity and the flow guiding groove (11) at one end facing the liquid supply arm. A third spring is sleeved on the outside of the conduit (8), and the two ends of the third spring abut against the inner wall of the connecting pipe (1) and the side wall of the movable block (7) respectively. When the movable block (7) moves toward the liquid supply arm, the third spring is compressed and deformed.

10. The die-casting liquid supply stabilization mechanism as described in claim 9, characterized in that, The liquid guiding cavity includes a first flow channel (4), a second flow channel (5) and a third flow channel (6) sequentially connected in the connecting pipe (1) along the casting liquid conveying direction; the conduit (8) is slidably inserted in the third flow channel (6), and a piston ring (15) is provided on the outer wall of the conduit (8), and the piston ring (15) is in a sealing sliding fit with the inner wall of the third flow channel (6).

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