Grouting filling pump

Abstract

The invention discloses a grouting filling pump, and belongs to the technical field of grouting pumps, the grouting filling pump comprises at least four oil cylinder valve groups and pistons with moving strokes in the oil cylinder valve groups, and the pistons in the oil cylinder valve groups have a propelling state, a retreating state and a transition state between the propelling state and the retreating state; at any moment, at least two pistons are in a propelling state and a returning state respectively; the lifting valve is communicated with the oil cylinder valve groups, and the lifting valve controls opening and closing of a valve seat of the lifting valve through a valve clack. In the oil cylinder valve group, each piston is continuously switched in three stroke states, and at any moment, pistons distributed in different states, particularly pistons distributed in a propelling state and a returning state, exist in the whole oil cylinder valve group system, so that a slurry feeding action and a slurry discharging action exist in the whole pumping system at each moment; and the continuity of the slurry feeding and grouting process of the lifting valve can be ensured.

Description

Technical Field

[0001] The invention belongs to the technical field of grouting pumps, in particular to a grouting filling pump. Background Art

[0002] Layer grouting pumps are critical equipment in coal mine water prevention, foundation reinforcement, and settlement control projects. Their core function is to inject cement slurry or chemical slurry into the layer of ground at high pressure to achieve filling and reinforcement. Currently, the industry generally uses specialized diaphragm pumps or high-pressure grouting pumps. While these pumps can meet basic grouting needs, they present challenges such as high equipment purchase costs, short service life of key wear parts (such as diaphragms and valve blocks), and frequent maintenance.

[0003] To reduce costs, the industry has recently attempted to leverage proven equipment from the tailings paste filling industry, replacing traditional aeration grouting pumps with industrial filling pumps. The tailings filling industry primarily utilizes two types of industrial filling pumps: the S-shaped swing valve type and the poppet valve type. While these two types differ in structure (the former relies on a swing valve to switch the flow path left and right, while the latter relies on the up-and-down movement of a poppet valve), their core operating principle is based on alternating dual-cylinder propulsion. The pump body is equipped with two independent plunger-type delivery cylinders. Slurry is distributed from the hopper through the pump head and alternately drawn into the left and right delivery cylinders, where it is then pushed out by pistons under pressure. A key feature is that the pistons of the two delivery cylinders move in exact sync and in opposite phases. That is, when the piston of one cylinder reaches the end of its delivery stroke, the piston of the other cylinder is at the end of its intake stroke, and both cylinders switch directions at the same instant.

[0004] However, this fully synchronized reversing mechanism, when applied to delamination grouting, exposes an inherent defect that is difficult to overcome: at the moment of synchronous piston reversal, the slurry pressure in the pipeline drops sharply to zero, resulting in periodic and violent pulsation of the slurry pressure throughout the entire transportation process. Periodic pressure shocks cause strong vibrations and even resonance in the transportation pipeline, accelerating fatigue damage to the pipeline and joints, posing a safety hazard and requiring frequent maintenance and reinforcement. The grouting process requires stable and continuous penetration and diffusion of the slurry within the target delamination layer. Instantaneous pressure loss not only interrupts the grouting process, but is also likely to cause backflow of the injected slurry or closure of delamination cracks, seriously affecting the uniformity and density of the grouting body and the ultimate reinforcement and anti-seepage effects.

[0005] The operating principle of a swash plate piston pump is based on the relative motion between a rotating cylinder block and an inclined swash plate, which generates reciprocating motion of the piston within the cylinder bore. Importantly, the multiple pistons in a swash plate piston pump can be simultaneously in different stages of the suction or pressure stroke, resulting in a very stable output flow and minimal pulsation. However, swash plate piston pumps are characterized by short piston strokes, high reciprocating frequency, and significant wear on the valve assembly, resulting in a short service life and high maintenance costs. Summary of the Invention

[0006] The purpose of the present invention is to provide a grouting filling pump to solve the problems raised in the above-mentioned prior art.

[0007] A grouting filling pump is provided, comprising: At least four cylinder valve groups and a piston having a movable stroke in each cylinder valve group, wherein the piston has an advancing state, a retracting state, and a transition state between the advancing state and the retracting state in the cylinder valve group; At any moment, there is at least one piston in the advancing state and at least one piston in the retracting state; A batching pump head and a discharge pump head that can be interconnected, wherein the batching pump head connects multiple oil cylinder valve groups to each other, and every two oil cylinder valve groups form a paired group; The swing valve includes a valve core, a valve shaft, a swing arm and two execution push cylinders. The valve core is used to switch the communication status between the two cylinder valve groups in a single pairing group and the discharge pump head. A rotating pair is formed between the valve shaft and the batching pump head. One end of the valve shaft is used to execute the swing of the valve core, and the other end of the valve shaft is connected to the two execution push cylinders through the swing arm.

[0008] As a further solution of the present invention: the number of the oil cylinder valve groups is an even number.

[0009] By pairing and grouping all cylinders, structural symmetry and kinematic coordination are achieved, facilitating dynamic balance and tachological planning in mechanical design. This design simplifies control system logic, improves overall operational balance and structural compactness, ensures a stable feed and discharge combination at all times, and enhances grouting consistency. The symmetrical design reduces the difficulty of synchronous control and facilitates distributed control or modular multi-cylinder control.

[0010] As a further solution of the present invention: every two oil cylinder valve groups form a pairing group and the pairing process traverses all oil cylinder valve groups; At any moment, the two pistons in the paired group are respectively in the advancing state and the retracting state, or the two pistons in the paired group are simultaneously in the transition state.

[0011] This design establishes a control logic that achieves "local synchronous counteraction" but "overall peak-shifting coordination." The two pistons in the same paired group operate in opposite or intermediate transition states, ensuring flow continuity within the group. Different paired groups operate in staggered peaks to avoid large pressure fluctuations and maintain system-wide rhythm coordination and energy balance. By reducing local load peaks, system reliability is improved and wear on pistons and valve bodies is reduced.

[0012] As a further solution of the present invention, a stroke cycle is defined as a piston sequentially traversing a single-stroke transition state, a propulsion state, and a retraction state. At the same travel speed, multiple pairing groups sequentially start the stroke cycle.

[0013] This design creates operating rhythm differences between multiple paired groups, keeping the pistons in different phases. Multiple paired groups start sequentially, avoiding the accumulation of system load peaks caused by in-phase movement and creating a continuous staggered movement rhythm. This arrangement significantly smooths flow fluctuations, reduces sudden and drastic flow changes, and improves system response stability and durability.

[0014] As a further solution of the present invention: a plurality of pairing groups start the travel cycles in sequence at the same time intervals.

[0015] By forming an equidistant staggered movement rhythm and ensuring an equidistant phase difference between cylinder operations, the periodic pumping behavior can be considered to be evenly distributed throughout the entire operating cycle, forming an equal flow output close to continuous pumping, further weakening the slurry pressure pulsation and improving the grouting uniformity.

[0016] As a further solution of the present invention: when the piston is in the advancing state, the corresponding oil cylinder valve group and the discharge pump head are in a communicating state; When the piston is in the retreat state, the corresponding oil cylinder valve group and the batching pump head are in a communication state.

[0017] The batching pump head acts as a transfer bin to realize the logical switching of fluid direction and pressure state. The connection state with the cylinder valve group or the discharge pump head is determined by the piston displacement state, forming a structural conduction switching mechanism to realize synchronous feeding and discharging action switching.

[0018] As a further solution of the present invention: the inner cavity of the dosing pump head is annular, and a plurality of the dosing cavities are arranged along the circumference of the dosing pump head.

[0019] Mirroring the annular arrangement of the multiple dispensing chambers, the multiple cylinder valve groups are also arranged circumferentially. The filling pump's circumferential arrangement of multiple cylinder groups enhances space compactness compared to a transverse arrangement, and the greater the number of cylinder valve groups, the more effective the integration. Furthermore, the circumferential arrangement shortens the path between each dispensing chamber and the discharge port of the discharge pump head, minimizing pressure loss. As a further solution of the present invention: the oil cylinder valve group also includes a delivery cylinder and a main oil cylinder, the main oil cylinder drives the piston to move in the delivery cylinder, a water washing chamber is provided between the delivery cylinder and the main oil cylinder, and the piston moves through the water washing chamber.

[0020] The main cylinder provides power, while the delivery cylinder propels the liquid. During movement, the piston comes into contact with the coolant in the wash chamber for cooling, preventing the piston from heating up due to high-pressure operation, effectively extending the life of the seals, and avoiding deformation or leakage caused by temperature differences.

[0021] Compared with the prior art, the present invention has the following beneficial effects: 1. In the oil cylinder valve group, each piston continuously switches within three stroke states, and at any moment, there are pistons in different states distributed in the entire oil cylinder valve group system, especially pistons in the advancing state and the retreating state. Therefore, there are slurry feeding and slurry discharging actions at every moment in the entire pumping system, which can ensure the continuity of the slurry feeding and grouting process of the lifting valve.

[0022] 2. Multiple cylinder valve groups operate alternately to form a multi-cylinder staggered rhythm, maintaining pressure fluctuations within a smaller range, avoiding the instantaneous pressure loss caused by traditional double-cylinder alternating rotation, and thus significantly reducing pressure pulsation, making the entire pumping process more stable and controllable.

[0023] 3. The cylinder valve group provides pumping driving force through the hydraulically driven piston. The piston can have a large pumping stroke in the cylinder valve group. Therefore, the entire filling pump system has the characteristics of large piston stroke and low reciprocating frequency. Combined with the continuous and stable grouting achieved by the alternating operation of multiple cylinders, the wear rate of the valve group is significantly reduced, the service life of the filling pump is increased, and the maintenance rate is reduced.

[0024] 4. The swinging motion of the swing valve synchronously controls the opening and closing of the inlet and outlet channels of the two cylinder valve groups, reliably controlling the timing of inlet and outlet according to the corresponding piston's operating state. The inlet and outlet channels of each cylinder valve group are integrated into the batching pump head, facilitating centralized replenishment of slurry. The valve shaft serves as a transmission element, driving the valve core to swing within the batching pump head. It also enables the external design of the swing arm and actuator cylinder, transmitting torque while preventing contact between the swing arm and actuator cylinder and the slurry. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the embodiments of the present drawings or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present drawings. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0026] Figure 1 This is one of the structural diagrams of the grouting filling pump in Example 3; Figure 2 This is the second structural diagram of the grouting filling pump in Example 3; Figure 3This is the third structural diagram of the grouting filling pump in Example 3; Figure 4 It is the control logic of the oil cylinder valve group and the oil flow adjustment curve; Figure 5 This is one of the structural diagrams of the grouting filling pump in Example 4; Figure 6 This is the second structural diagram of the grouting filling pump in Example 4; Figure 7 This is the third structural diagram of the grouting filling pump in Example 4.

[0027] In the figure: 1. Cylinder valve group; 11. Piston; 111. First piston; 112. Second piston; 113. Third piston; 114. Fourth piston; 12. Delivery cylinder; 13. Main cylinder; 2. Dosing pump head; 21. Dosing chamber; 22. Feed valve seat; 23. Discharge valve seat; 3. Discharge pump head; 4. Feed hopper; 51. Vertical cylinder; 52. Feed valve disc; 61. Horizontal cylinder; 62. Discharge valve disc; 7. Swing valve; 71. Valve core; 72. Valve shaft; 73. Swing arm; 74. Execution push cylinder; 8. Washing chamber. DETAILED DESCRIPTION

[0028] In order to make the purpose, technical solutions and advantages of this application more clearly understood, the present application is described and illustrated below in conjunction with the accompanying drawings and examples. It should be understood that the specific embodiments described herein are merely used to explain this application and are not intended to limit this application. Based on the embodiments provided in this application, all other embodiments obtained by those of ordinary skill in the art without making any creative efforts are within the scope of protection of this application.

[0029] Obviously, the drawings described below are merely examples or embodiments of the present application. Those skilled in the art can, without inventive effort, apply the present application to other similar scenarios based on these drawings. Furthermore, it is also understood that, although the effort involved in such a development process may be complex and lengthy, for those skilled in the art related to the content disclosed in this application, changes in design, manufacturing, or production based on the technical content disclosed in this application are merely conventional technical means and should not be construed as an insufficiency of the content disclosed in this application.

[0030] However, unnecessary detailed descriptions may be omitted. For example, detailed descriptions of well-known matters and repetitive descriptions of substantially identical structures may be omitted. This is to avoid unnecessary redundancy in the following description and to facilitate understanding by those skilled in the art. Furthermore, the drawings and the following description are provided to facilitate a thorough understanding of this application by those skilled in the art and are not intended to limit the subject matter recited in the claims.

[0031] See also Figure 5-Figure 7 As shown, in an embodiment of the present invention, a grouting filling pump includes at least four cylinder valve groups 1 and a piston 11 with a moving stroke in each cylinder valve group 1, the piston 11 has a propulsion state, a retraction state and a transition state between the propulsion state and the retraction state in the cylinder valve group 1; at any moment, there are at least two pistons 11 that are respectively in the propulsion state and the retraction state; and it also includes a lifting valve, which is connected to multiple cylinder valve groups 1, and the valve disc of the lifting valve controls the opening and closing of the valve seat through linear motion.

[0032] In addition to piston 11, cylinder valve assembly 1 also includes a delivery cylinder 12 and a master cylinder 13. Delivery cylinder 12 and master cylinder 13 are connected to form a continuous travel channel. Piston 11 is the output rod of master cylinder 13, and piston 11 is driven by master cylinder 13 to reciprocate within delivery cylinder 12. It should be noted that the advance state of piston 11 is from point A to point B of delivery cylinder 12; the retraction state of piston 11 is from point B to point A of delivery cylinder 12; and the transition state of piston 11 is when it switches direction between points A and B.

[0033] In one embodiment, there are three cylinder valve groups 1. In this embodiment, at any given moment, at least one of the three pistons 11 is in the advancing state and at least one is in the retracting state. Furthermore, when one piston 11 is in the transition state, the other two pistons 11 are necessarily in the advancing and retracting states, respectively. This means that to prevent transient pressure loss and periodic pressure pulsations caused by alternating rotations between the two cylinders, the minimum number of cylinder valve groups 1 is three.

[0034] Specifically, the pumping system always contains a collection of cylinder valve groups 1 whose operating cycles are staggered and distributed at different phases within the cycles. In addition to the above-mentioned embodiments, the number of cylinder valve groups 1 arranged in the present invention can be greater than three. The greater the number of cylinder valve groups 1, the closer the propulsion and retraction behavior of the entire system is to continuous linear rather than square wave alternation. During each short period of time, some cylinder valve groups 1 are in the propulsion state, and the slurry output continues to flow. The arrangement of multiple cylinder valve groups 1 has natural redundancy. Even if a cylinder fails, becomes stuck, or is removed for maintenance, the remaining cylinders can still maintain basic system operation. Therefore, the number of cylinder valve groups 1 arranged in the present invention is preferably greater than three.

[0035] In one embodiment, the number of cylinder valve groups 1 is an even number. The even number of cylinder valve groups 1 provides a basis for forming multiple pairs of the same group, such as when the number of cylinder valve groups 1 is four, two cylinder valve groups 1 form a local antagonistic group, and the two groups form an overall staggered peak coordination; or when the number of cylinder valve groups 1 is six, three cylinder valve groups 1 form a local antagonistic group, and the two groups form an overall staggered peak coordination; or when the number of cylinder valve groups 1 is six, two cylinder valve groups 1 form a local antagonistic group, and the three groups form an overall staggered peak coordination, thereby forming a multi-system symmetrical unit. It should be noted that the local antagonistic group here, that is, multiple pistons 11 form a regular flow waveform in a single pairing group, and the phases of multiple local antagonistic groups are staggered so that the output flow is closer to a constant value after superposition.

[0036] Example 1 Every two cylinder valve groups 1 form a pairing group and the pairing process traverses all cylinder valve groups 1. At any moment, the two pistons 11 in the pairing group are respectively in the advancing state and the retreating state, or the two pistons 11 in the pairing group are in the transition state at the same time.

[0037] It should be noted that the two pistons 11 in the above-described embodiments, respectively being in the advancing state and the retracting state, or simultaneously being in the transition state, should not be interpreted as a choice between two matching modes, but rather as the states in which they are in a certain operating phase. Specifically, during operation of the charging pump, the two pistons 11 of a single paired group can have two states during a certain cycle phase: one piston 11 is in the advancing state while the other is in the retracting state, and one piston 11 is in the transition state while the other is also in the transition state.

[0038] The above solution achieves the following benefits: through mechanical linkage or control program-enforced interlocking of the pistons 11 within a group, a localized flow self-balancing unit is formed. When the two cylinders simultaneously enter the transition state (the moment of reversal), the other paired group is already discharging or absorbing slurry, maintaining the system pressure from returning to zero. This design of internal complementarity and inter-group interaction achieves a stable and continuous slurry flow, eliminating the risk of slurry backflow during separation grouting.

[0039] Furthermore, the symmetrical structure allows for redundant paired groups, with hydraulic lines automatically switching in the event of a failure. This means that if a paired group fails due to piston 11 seal failure or valve jamming, the inlet and outlet valves of the failed group are closed, locking the failed group's piston 11 in a transitional state. The hydraulic system switches to bypass mode, allowing the remaining even-numbered cylinder groups to continue pairing and maintain the remaining operating pressure. This design essentially creates a redundant array. If a single paired group fails, the system maintains uninterrupted slurry delivery service by redistributing hydraulic data flows. The topologically symmetrical design ensures rapid system reconfiguration.

[0040] Example 2 A stroke cycle consists of a piston 11 sequentially traversing a single transition state, advancing state, and retracting state. Multiple pistons 11 initiate stroke cycles sequentially at the same travel speed. This solution discretely distributes the piston 11 state switching points along the time axis. The flow functions of each cylinder are staggered in the time domain, filling in troughs and effectively suppressing pipeline resonance.

[0041] Furthermore, multiple pistons 11 sequentially initiate their stroke cycles at the same time intervals. The group of pistons 11 is considered a vibration system with equidistant phase distribution, so that the state switching points of each cylinder are evenly distributed along the time axis. This design eliminates the time domain window where periodic energy accumulates in traditional pumping, and evenly distributes the mechanical impact energy originally concentrated at a specific moment throughout the entire operating cycle. Even if a cylinder fails unexpectedly, the remaining cylinders can automatically form a new equally spaced sequence. This self-healing capability based on time symmetry enables the system to maintain stable characteristics even during degraded operation, avoiding the vulnerability of traditional equipment to single-point failures and global collapse.

[0042] In a specific embodiment, a lift valve type cross-flow grouting pump composed of four cylinder valve groups 1 is provided. The working mode is that the main oil pump provides hydraulic oil to the main oil cylinder 13. The main oil cylinder 13 pushes the piston 11 to alternately move forward and backward in the delivery cylinder 12. When the piston 11 moves backward, the lift valve is in the material suction working state. When the piston 11 moves forward, the lift valve is in the material pushing state. The speed of the piston 11 is determined by the displacement of the main oil pump. The direction of the piston 11 is determined by the reversing valve of the hydraulic system. Each main oil cylinder 13 corresponds to a set of hydraulic power units, that is, one motor drives one main oil pump to drive one main oil cylinder 13. The four main oil cylinders 13 are all full-stroke displacement cylinders. The reversing signal comes from the position detection of the displacement cylinder, and each cylinder is controlled separately.

[0043] The grouting method specifically comprises the following steps: S1. Set the maximum stroke L of the piston 11. The four pistons 11 return to the displacement value "0" in sequence. The four hydraulic systems are started separately. S2. Activate the pumping button, and the first piston 111 begins to move forward. When the displacement value of the first piston 111 reaches 1 / 2L, the second piston 112 begins to move forward; when the displacement value of the second piston 112 reaches 1 / 2L, the third piston 113 begins to move forward; when the displacement value of the third piston 113 reaches 1 / 2L, the fourth piston 114 begins to move forward; S3. When the displacement value of the first piston 111 reaches "1", the displacement value of the reversing signal is triggered to start changing from "1" to "0". When the displacement value of the first piston 111 becomes "0", the displacement value of the reversing signal is triggered to start changing from "0" to "1", and the cycle repeats.

[0044] The switching logic of S4, the second piston 112, the third piston 113, and the fourth piston 114 is the same as that of the first piston 111, and will not be described in detail here.

[0045] In a more specific embodiment, in order to ensure that the lifting valve achieves constant flow and that the total delivery volume of multiple delivery cylinders 12 remains stable at all times, the propulsion speed of each delivery cylinder 12 is required to be variable (when the area remains unchanged, the speed is equal to the flow rate). In other words, the speed of each master cylinder 13 must be variable and controllable.

[0046] The specific control logic is: Oil pump working flow: Q 工作 ; Oil pump set flow rate: Q 设定 ; Minimum flow rate of oil pump: Q0; Maximum displacement of the master cylinder 13: L; Actual stroke of the master cylinder 13: X; When the piston 11 is fully retracted, it is calibrated to position 0; when the piston 11 is fully extended, it is calibrated to position 1; when calibrating the position, the front and rear buffer positions must be considered to avoid front and rear collision with the cylinder. The buffer distance is calibrated to: 80mm-90mm.

[0047] When X≤1 / 2L, Q 工作 The calculation formula is: Q 工作 =2X / L×Q 设定 +Q0×(L-2X) / L; When X>1 / 2L, Q 工作 The calculation formula is: Q 工作 =(2(LX) / L)×Q 设定 -Q0×(2X-L) / L; The grouting method specifically comprises the following steps: The first piston 111 advances to discharge material. When the first piston 111 advances from the "0" position to the "1 / 2L" position, the flow rate increases linearly. When the first piston 111 advances from the "1 / 2L" position to the "L" position, the discharge begins to decrease when it reaches 80mm-90mm from the "L" position. When the first piston 111 advances to the "1" position, the PLC sends a retract command for the first piston 111 to the electronically controlled reversing valve, causing the first piston 111 to move backward to absorb material. When the first piston 111 advances from the "L" position to the "1 / 2L" position, the flow rate increases linearly. When the first piston 111 advances from the "1 / 2L" position to the "0" position, the flow rate decreases linearly. The first piston 111 moves to "0" and awaits the next command. The reversing logic of the second piston 112, third piston 113, and fourth piston 114 is the same as that of the first piston 111 and will not be described in detail here.

[0048] Based on the above embodiment, the control logic of the electric control reversing valve of the cylinder valve group 1 and the flow adjustment curve of the master cylinder 13 are detailed in Figure 4 .

[0049] Example 3 See also Figure 1-Figure 3 As shown, the poppet valve includes a dosing pump head 2, a discharge pump head 3, and a feed hopper 4, which are interconnected. The dosing pump head 2 is formed with multiple dosing cavities 21 that communicate with corresponding cylinder valve groups 1. When the piston 11 is in the advancing state, the corresponding dosing cavity 21 is blocked from the feed hopper 4, while the corresponding dosing cavity 21 is in communication with the discharge pump head 3. When the piston 11 is in the retracted state, the corresponding dosing cavity 21 is in communication with the feed hopper 4, while the corresponding dosing cavity 21 is in a blocked state from the discharge pump head 3.

[0050] The displacement state of piston 11 determines the open / close of the flow path. Specifically, the advancing and retracting states of piston 11 constitute the operational logic controlling the connection between the batching chamber 21 and the inlet and outlet ports, creating mechanically enforced physical isolation. Driven by the corresponding piston 11 state, multiple batching chambers 21 simultaneously function as slurry suction and discharge chambers, achieving the spatiotemporal superposition of "slurry suction" and "slurry injection." Each batching chamber 21 is physically isolated by partitions to prevent slurry crosstalk.

[0051] Specifically, the valve disc includes a vertical cylinder 51, the valve seat includes a feed valve seat 22, the batching chamber 21 is connected to the feed hopper 4 through the feed valve seat 22, and the output end of the vertical cylinder 51 is provided with a feed valve disc 52 for opening and closing the feed valve seat 22. Each vertical cylinder 51 serves as an independent power source, and each feed valve disc 52 is driven by the corresponding vertical cylinder 51. The displacement state of the piston 11 in the cylinder valve group 1 triggers the action of the vertical cylinder 51, ensuring that the opening and closing of the channel between the feed hopper 4 and the batching chamber 21 is strictly synchronized with the state of the piston 11. The feed valve disc 52 and the feed valve seat 22 adopt a flat surface compression seal or a conical surface compression seal, and there is almost no wear and loss between the feed valve disc 52 and the feed valve seat 22.

[0052] Specifically, the valve disc comprises a horizontal cylinder 61, and the valve seat comprises a discharge valve seat 23. The dispensing chamber 21 communicates with the discharge pump head 3 via the discharge valve seat 23. A discharge valve disc 62 is provided at the output end of the horizontal cylinder 61, sealing the discharge valve seat 23. Each discharge valve disc 62 serves as an independent power source, and each inlet valve disc 52 is linearly driven by its corresponding horizontal cylinder 61. When the piston 11 enters the advancing state, the horizontal cylinder 61 is activated, ensuring that the opening and closing of the passage between the discharge pump head 3 and the dispensing chamber 21 is strictly synchronized with the state of the piston 11. The discharge valve disc 62 and the discharge valve seat 23 utilize a flat or conical surface compression seal, resulting in virtually no wear and tear between the discharge valve disc 62 and the discharge valve seat 23.

[0053] In one specific embodiment, the inner cavity of the dosing pump head 2 is annular, with multiple dosing chambers 21 arranged along the circumference of the dosing pump head 2. This reconfigures the traditional horizontally and vertically arranged linear flow channels into closed annular channels, creating a symmetrical centrifugal flow field. The multiple dosing chambers 21 are distributed at equal angles along the circumference and are evenly spaced around the circumference, ensuring consistent length of the pipeline from the actuator to the hydraulic control unit, and minimizing pressure transmission delay errors.

[0054] It should be noted that the filling pump structure provided in Example 3 can be controlled by the filling control methods of Examples 1 and 2 provided in the present invention.

[0055] Example 4 See also Figure 5-Figure 7 As shown, the poppet valve includes a dosing pump head 2 and a discharge pump head 3 that can communicate with each other. The dosing pump head 2 connects multiple cylinder valve groups 1. When the piston 11 is in the advancing state, the corresponding cylinder valve group 1 and the discharge pump head 3 are in a communication state; when the piston 11 is in the retracted state, the corresponding cylinder valve group 1 and the dosing pump head 2 are in a communication state.

[0056] The displacement state of piston 11 determines the flow path's open / closed state. Specifically, the advancing and retreating states of piston 1 constitute the operational logic controlling the connections between cylinder valve group 1 and the batching pump head, as well as between cylinder valve group 1 and discharge pump head 3, creating mechanically enforced physical isolation. A valve group control mechanism is established between cylinder valve group 1 and both batching pump head 2 and discharge pump head 3, enabling cylinder valve group 1 to switch between the slurry suction and discharge states, achieving the spatiotemporal superposition of "slurry suction" and "grouting" actions.

[0057] Specifically, every two cylinder valve groups 1 form a pairing group, and the valve disc includes a swing valve 7. One end of the swing valve 7 is rotatably connected to the ingredient pump head 2 and communicated with the discharge pump head 3, and the other end of the swing valve 7 can be respectively communicated with the two cylinder valve groups 1 in a single pairing group through swinging.

[0058] The spool 71 of the swing valve 7 comprises a fluid flow channel and includes a first horizontally extending section, an inclined extending section, and a second horizontally extending section, which extend sequentially. The first horizontally extending section of the spool 71 rotates about the rotary assembly on the dosing pump head 2, ensuring that this end remains connected to the discharge pump head 3. Driven by the fixed-axis rotation and the swing arm structure formed by the inclined extending section, the second horizontally extending section of the spool 71 can swing between the two cylinder valve groups 1 within a single paired group, thereby switching the connection between the cylinder valve groups 1.

[0059] Specifically, when the valve core 71 rotates to connect with a certain oil cylinder valve group 1, the corresponding piston 11 is in the advancing state, and the fluid is delivered to the discharge pump head 3 through the valve core 71, realizing the slurry suction action. When the other oil cylinder valve group 1 in the paired group is connected with the feed pump head 2, the corresponding piston 11 is in the retreating state, and the fluid is delivered to the oil cylinder valve group 1 through the feed pump head 2, realizing the slurry injection action. The slurry suction action and slurry injection action are switched back and forth, realizing continuous feeding of the poppet valve.

[0060] To facilitate batching and feeding, the present invention integrates multiple cylinder valve groups 1 within a single batching pump head 2, forming a complete pumping system. Within this system, each paired group controls its connection to the discharge pump head 3 via a corresponding valve core 71. To prevent the drive element that swings the valve core 71 from contact with the slurry within the batching pump head 2, which would affect its operation and reduce its lifespan, the present invention employs an external design.

[0061] More specifically, the outer wall of the valve core 71 is connected to a valve shaft 72 coaxial with the axis of the rotary countershaft. The other end of the valve shaft 72 passes through the dosing pump head 2, forming a rotary countershaft with the dosing pump head 2. A swing arm 73 is provided at the through-end of the valve shaft 72. The extended ends of the swing arm 73 are respectively connected to the output shafts of two actuator push cylinders 74. The two actuator push cylinders 74 perform simultaneous telescoping movements to drive the swing arm 73 to swing. The swing of the swing arm 73 drives the valve shaft 72 to rotate, and the valve shaft 72 in turn drives the valve core 71 to swing, realizing the switching of the communication state of the cylinder valve group 1.

[0062] The valve shaft 72 serves as a torque transmission link between the valve core 71 in the system space and the swing arm 73 and the execution push cylinder 74 outside the system space, realizing the external design of multiple swing arm 73 and execution push cylinder 74 drive groups, effectively ensuring the stable operation of each mechanism.

[0063] It should be noted that the filling pump structure provided in Example 4 can be controlled by the filling control method of Example 1 provided in the present invention. In addition, it can also be controlled by the filling control method of Example 2, that is, in the structure of Example 4, the two pistons 11 in each pairing group have a symmetrical operating logic, that is, when one is in the slurry suction state, the other is in the grouting state, or they are in the steering state at the same time. Therefore, the specific operating mechanism between multiple pairing groups is that the piston 11 sequentially traverses the transition state, propulsion state, and retraction state of a single trip as a stroke cycle. At the same travel speed, multiple pairing groups start the stroke cycle in sequence. Furthermore, multiple pairing groups start the stroke cycle in sequence at the same time interval.

[0064] A water washing chamber 8 is provided between the delivery cylinder 12 and the main oil cylinder 13. The piston 11 directly penetrates the coolant cavity of the water washing chamber 8. When the piston 11 moves, the surface can be immersed in the turbulent coolant to conduct away friction heat and compression heat.

[0065] It should be noted that the present application is not limited to the above-mentioned embodiments. The above-mentioned embodiments are merely examples, and any embodiments having substantially the same structure and effect as the technical concept within the scope of the present application are all included in the technical scope of the present application. In addition, without departing from the scope of the present application, any other embodiments that can be conceived by those skilled in the art and that combine some of the constituent elements in the embodiments are also included in the scope of the present application.

Claims

1. A grouting filling pump, characterized in that: include: At least four oil cylinder valve groups (1) and a piston (11) having a movable stroke in each oil cylinder valve group (1), wherein the piston (11) has an advancing state, a retracting state, and a transition state between the advancing state and the retracting state in the oil cylinder valve group (1); At any moment, there is at least one piston (11) in an advancing state and at least one piston (11) in a retracting state; A dosing pump head (2) and a discharging pump head (3) that can be interconnected, wherein the dosing pump head (2) connects a plurality of oil cylinder valve groups (1) to each other, and every two oil cylinder valve groups (1) form a paired group; A swing valve (7) comprises a valve core (71), a valve shaft (72), a swing arm (73) and two execution push cylinders (74), wherein the valve core (71) is used to switch the communication state between the two oil cylinder valve groups (1) in a single paired group and the discharge pump head (3), a rotary pair is formed between the valve shaft (72) and the batching pump head (2), one end of the valve shaft (72) is used to swing the execution valve core (71), and the other end of the valve shaft (72) is connected to the two execution push cylinders (74) through the swing arm (73).

2. A grouting filling pump according to claim 1, characterized in that: Every two oil cylinder valve groups (1) form a pairing group and the pairing process is carried out throughout all the oil cylinder valve groups (1); At any moment, the two pistons (11) in the paired group are respectively in the advancing state and the retreating state, or the two pistons (11) in the paired group are simultaneously in the transition state.

3. A grouting filling pump according to claim 1, characterized in that: A stroke cycle is defined as the piston (11) sequentially traversing a single-stroke transition state, a propulsion state, and a retraction state. At the same travel speed, multiple paired groups sequentially start the stroke cycle.

4. A grouting filling pump according to claim 3, characterized in that: Multiple paired groups start the travel cycle in sequence at the same time interval.

5. A grouting filling pump according to claim 1, characterized in that: When the piston (11) is in the advancing state, the corresponding oil cylinder valve group (1) and the discharge pump head (3) are in a communicating state; When the piston (11) is in the retracted state, the corresponding oil cylinder valve group (1) and the dosing pump head (2) are in a connected state.

6. A grouting filling pump according to claim 1, characterized in that: The oil cylinder valve group (1) further comprises a delivery cylinder (12) and a main oil cylinder (13). The main oil cylinder (13) drives the piston (11) to move in the delivery cylinder (12). A water washing chamber (8) is provided between the delivery cylinder (12) and the main oil cylinder (13). The piston (11) moves through the water washing chamber (8).

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