High viscosity emulsion explosive plunger type transfer pump and working method thereof

Abstract

The application discloses a high-viscosity emulsion explosive plunger type conveying pump and a working method thereof. The conveying pump comprises a driving power head, a lower pump body, a conveying piston rod assembly, an inlet one-way valve, an outlet one-way valve, a position sensing assembly and a stroke buffering assembly. The position sensing assembly is used for detecting the actual movement stroke of the conveying piston rod assembly. The stroke buffering assembly comprises a pilot oil path control buffer and an electro-hydraulic reversing valve buffering assembly which respectively act on the hydraulic oil paths on both sides of the power head. During conveying, the material is sucked by negative pressure, and the piston rod assembly is controlled to discharge the material in sections and stop at the intermediate position according to the target charge quantity of the blast hole. According to the residual storage state, the material is continuously discharged or reversely supplemented. The conveying pump can reduce the hydraulic impact and inertial displacement in the intermediate stop position and the reversing process, and improve the stability and accuracy of the continuous sectional conveying and charge control of the high-viscosity emulsion explosive.

Description

Technical Field

[0001] This invention relates to the field of pumping equipment technology, and in particular to a high-viscosity emulsion explosive plunger pump and its working method. Background Technology

[0002] With the development of mechanized charging in underground mining and tunnel engineering, bulk emulsion explosives or latex matrix are gradually being used in borehole charging operations. Existing underground charging equipment typically uses a charging pump to directly draw emulsion explosives or latex matrix from the hopper and then transport the material into the borehole.

[0003] However, emulsion explosives and latex matrices have high viscosity and poor flowability. When using natural suction, the charging pump is prone to insufficient suction and incomplete filling of the pump chamber, leading to a decrease in pump volumetric efficiency. Simultaneously, factors such as material temperature and hopper level also affect the actual suction volume, causing fluctuations in the actual conveying volume for each conveying stroke, thus impacting the metering accuracy, continuity, and density of the charge. Especially for tunnel boring and horizontal runway blast holes, the single-hole charge is typically small, requiring high precision control over the conveying volume and stopping position. Existing conveying methods struggle to simultaneously meet the demands for reliable suction, continuous conveying, and quantitative charging of high-viscosity materials.

[0004] Furthermore, the plunger-type conveying mechanism requires frequent starts, stops, and reversals during operation. When the piston assembly stops or changes direction in the middle of its stroke, the pressure and flow rate in the hydraulic system change rapidly, and the inertia of the moving parts themselves can easily cause deviations in the stopping position or reversal impacts. Therefore, how to improve the feeding stability of high-viscosity emulsion explosives and achieve more accurate segmented conveying and stable start-stop and reversal during continuous charging remains a problem that existing conveying equipment needs to further solve. Summary of the Invention

[0005] This invention aims to at least partially solve one of the technical problems in related technologies. Therefore, one objective of this invention is to provide a plunger-type delivery pump for high-viscosity emulsion explosives and its operating method, which can reduce hydraulic shock and inertial displacement during intermediate stops and reversals, and improve the stability and accuracy of continuous segmented delivery and loading control of high-viscosity emulsion explosives.

[0006] In a first aspect, the present invention provides a high-viscosity emulsion explosive plunger delivery pump, comprising a drive power head, a lower pump body, a delivery piston rod assembly, an inlet check valve, an outlet check valve, a position sensing assembly, and a stroke buffer assembly. The drive head is connected to the conveying piston rod assembly. One end of the conveying piston rod assembly is connected to a lower pump body piston. The lower pump body piston is slidably disposed in the lower pump body so as to change the storage space of the lower pump body through the reciprocating motion of the lower pump body piston. The inlet check valve and the outlet check valve are respectively disposed on the feed side and the discharge side of the lower pump body. The inlet check valve includes a check valve plate that opens when the storage space forms a negative pressure and a limiting structure that limits the opening stroke of the check valve plate. The outlet check valve opens when the material in the storage space is pressurized. The position sensing component includes a fixed detection element and a movable detection element that move with the piston of the drive head, and is used to detect the actual stroke of the conveying piston rod assembly based on the relative displacement between the fixed detection element and the movable detection element. The stroke buffer assembly includes a first pilot oil circuit control buffer, a second pilot oil circuit control buffer, and an electro-hydraulic directional valve buffer assembly for adjusting the reversing process of the drive power head. The first pilot oil circuit control buffer and the second pilot oil circuit control buffer act on the hydraulic oil circuits on both sides corresponding to the forward and reverse movements of the drive power head, respectively, to absorb hydraulic shocks and balance pressure. The position sensing component cooperates with the stroke buffer component to enable the conveying piston rod assembly to stop at the middle position of the complete discharge stroke, and to continue moving in the discharge direction or in the opposite direction of the suction direction from the middle position.

[0007] Preferably, a high-pressure Gladge ring is provided in the middle of the side wall of the lower pump body piston, and irregularly shaped guide rings are embedded at the upper and lower ends of the lower pump body piston. The irregularly shaped guide rings slide in cooperation with the inner wall of the lower pump body. The high-pressure Gladge ring and the irregularly shaped guide rings together maintain the sealing state during the reciprocating motion of the lower pump body piston, so as to form a negative pressure for opening the inlet check valve when the lower pump body piston moves along the suction direction.

[0008] Preferably, the inlet check valve includes an inlet check valve seat, a check valve plate, and a valve plate limiting rod. The inlet check valve seat has a feed channel communicating with the storage space of the lower pump body. The check valve plate is movably disposed on the side of the inlet check valve seat facing the storage space and is detachably sealed with the inlet check valve seat. The valve plate limiting rod is disposed in the opening direction of the check valve plate and is used to limit the opening stroke when the check valve plate is separated from the inlet check valve seat.

[0009] Preferably, the outlet check valve includes an outlet valve seat, an outlet valve core, a steel ball, and a return spring. The outlet valve core is disposed within the outlet valve seat. The outlet valve seat has a lower step at the inlet of the outlet valve core, and the lower step has a sealing surface adapted to the outer surface of the steel ball. The outlet valve core has a spring mounting groove on the side near the outlet, and the return spring is disposed in the spring mounting groove and abuts against the steel ball to seal the steel ball against the lower step. The outlet valve core also has an upper step located on the side of the steel ball away from the lower step, and the upper step is used to limit the displacement of the steel ball when it moves away from the lower step. The abutting portion of the upper step opposite to the steel ball has a petal-shaped flow portion recessed towards the interior of the outlet valve core, so that the steel ball moves to the upper step under the action of material pressure and compresses the return spring.

[0010] Preferably, a ball-head self-aligning transmission structure is provided between the driving power head and the conveying piston rod assembly. The ball-head self-aligning transmission structure includes a ball-head rod, a ball-head limiting plate, and a ball-head seat. One end of the ball-head rod is connected to the power head piston rod of the driving power head, and the other end of the ball-head rod is provided with a ball head. The ball-head seat is provided with a spherical support portion adapted to the ball head. The ball head is movably accommodated within the ball-head seat and forms a spherical fit with the spherical support portion. The end of the ball-head seat away from the spherical support portion is connected to the conveying piston rod assembly. The ball head is connected to the ball head on the side away from the ball support and is connected to the cue seat. The ball head limiting plate has a limiting hole for the ball head to pass through. The limiting hole is used to limit the ball head from disengaging from the cue seat. A clearance is left between the ball head and the limiting hole to allow the ball head to swing relative to the cue seat, so that the ball head and the cue seat can compensate for the axial deviation between the drive head and the lower pump body by relative swinging during the transmission of axial driving force.

[0011] Preferably, a sleeve positioning assembly is provided between the drive power head and the lower pump body. The opposite ends of the drive power head and the lower pump body are respectively provided with mounting flanges, and the two mounting flanges are provided with opposing positioning holes. The sleeve positioning assembly includes a hollow limiting rod and a screw rod passing through the hollow limiting rod. The hollow limiting rod is disposed between the two mounting flanges, and both ends of the hollow limiting rod extend into the positioning holes of the two mounting flanges and form a positioning fit with the corresponding positioning holes to limit the radial relative displacement between the drive power head and the lower pump body. The screw rod passes through the hollow limiting rod axially and connects the two mounting flanges to limit the axial separation of the two mounting flanges. Thus, the drive power head and the lower pump body are installed and positioned through the fit between the hollow limiting rod and the two positioning holes.

[0012] Preferably, the drive power head has a first working oil circuit and a second working oil circuit respectively connected to the hydraulic chambers on both sides of the power head piston. The first pilot oil circuit control buffer and the second pilot oil circuit control buffer are respectively disposed in the first working oil circuit and the second working oil circuit. The first pilot oil circuit control buffer and the second pilot oil circuit control buffer each include a buffer overflow valve and a replenishing check valve. The buffer overflow valve is disposed on a pressure relief branch connected to the corresponding working oil circuit, so as to open the pressure relief branch when the oil pressure of the corresponding working oil circuit reaches the set pressure of the buffer overflow valve. The replenishing check valve is disposed on a replenishing branch connected to the corresponding working oil circuit, and the conduction direction of the replenishing check valve is towards the corresponding working oil circuit, so as to allow hydraulic oil to enter the corresponding working oil circuit through the replenishing branch and restrict the hydraulic oil from flowing in the opposite direction.

[0013] Preferably, the electro-hydraulic directional valve buffer assembly includes a hydraulic directional valve, a directional control unit, and two throttles; the hydraulic directional valve has an oil supply port, an oil return port, and a first working oil port and a second working oil port respectively connected to the first working oil circuit and the second working oil circuit; the valve core of the hydraulic directional valve forms a first hydraulic control chamber and a second hydraulic control chamber at its two ends; the valve core is movable between a first directional position and a second directional position; when the valve core is in the first directional position, the oil supply port is connected to the first working oil port, and the second working oil port is connected to the oil return port; when the valve core is in the second directional position, the oil supply port is connected to the second working oil port, and the first working oil port is connected to the oil return port; the directional control unit has a first control interface and a second control interface; the first control interface is connected to the first hydraulic control chamber through a first control oil circuit, and the second control interface is connected to the first hydraulic control chamber through a first control oil circuit. The two control oil circuits are connected to the second hydraulic control chamber, and the two throttles are respectively connected in series in the first control oil circuit and the second control oil circuit. The reversing control unit has two control states. In one control state, the first control interface serves as the control oil inlet and the second control interface serves as the control oil return, allowing control oil to enter the first hydraulic control chamber through the first control oil circuit and the corresponding throttle, while simultaneously allowing control oil in the second hydraulic control chamber to be discharged through the second control oil circuit and the corresponding throttle, and the valve core moves to the first reversing position. In the other control state, the first control interface serves as the control oil return and the second control interface serves as the control oil inlet, allowing control oil to enter the second hydraulic control chamber through the second control oil circuit and the corresponding throttle, while simultaneously allowing control oil in the first hydraulic control chamber to be discharged through the first control oil circuit and the corresponding throttle, and the valve core moves to the second reversing position.

[0014] Secondly, the present invention provides a method for operating a high-viscosity emulsion explosive plunger delivery pump, comprising any of the above-mentioned high-viscosity emulsion explosive plunger delivery pump solutions, wherein the operating method is as follows: S1: Drive the conveying piston rod assembly to move along the suction direction, which increases the storage space of the lower pump body and forms a negative pressure. The inlet check valve opens under the action of the negative pressure. The outlet check valve relies on the weight of the steel ball and the return spring to provide a downward elastic force to make the steel ball contact the lower step sealing surface of the outlet valve seat and close the outlet check valve, so as to suck the high viscosity emulsion explosive into the storage space. S2: Drive the conveying piston rod assembly to move along the discharge direction according to the target charge amount of the current borehole. This causes the valve plate of the inlet check valve to be pressed down by the hydraulic force generated by the material flow and contact the sealing surface of the inlet check valve seat, thus closing the inlet check valve and opening the outlet check valve. The actual movement stroke of the conveying piston rod assembly is detected by the position sensing component. When the actual movement stroke reaches the discharge stroke corresponding to the target charge amount of the current borehole, the conveying piston rod assembly stops at the middle position of the complete discharge stroke, and the undischarged high-viscosity emulsion explosive is retained in the storage space. S3: After the material discharge of the current borehole is completed, the subsequent operation mode is determined according to the remaining material status corresponding to the current stop position of the conveying piston rod assembly and the target charge amount of the next borehole. If the remaining material is greater than or equal to the target charge amount of the next borehole, step S2 is executed; if the remaining material is less than the target charge amount of the next borehole, step S4 is executed. S4: Move the conveying piston rod assembly in the opposite direction from the current stop position along the suction direction, and replenish the material while retaining the high-viscosity emulsion explosive already in the storage space. After the replenishment is completed, proceed to step S5. S5: Repeat steps S2-S4 until all boreholes are loaded with explosives.

[0015] Preferably, when the conveying piston rod assembly stops at the middle position of the complete discharge stroke, the hydraulic shock in the working oil circuit corresponding to the drive power head is buffered by the first pilot oil circuit control buffer and the second pilot oil circuit control buffer; when the conveying piston rod assembly moves in the opposite direction along the suction direction from the middle position, the hydraulic shock generated during the reversing process of the drive power head is buffered by the first pilot oil circuit control buffer and the second pilot oil circuit control buffer, and the movement speed of the valve core of the hydraulic reversing valve between the two reversing positions is limited by the throttle of the electro-hydraulic reversing valve buffer assembly.

[0016] The beneficial effects of this invention are: (1) The reciprocating motion of the piston in the lower pump body forms a storage space, and the inlet check valve and outlet check valve are used to realize the suction and discharge of high viscosity emulsion explosives, which is conducive to improving the stability of the suction and conveying process of high viscosity materials. (2) By detecting the actual movement stroke of the conveying piston rod assembly through the position sensing component, the conveying piston rod assembly can stop at the middle position of the complete discharge stroke according to the target charge amount of the blast hole, thereby realizing segmented quantitative discharge and retaining the undischarged emulsion explosive in the lower pump body, which facilitates the continuous completion of the charge of multiple blast holes. (3) After the current borehole discharge is completed, the discharge can be continued or the material can be replenished from the current middle position according to the remaining material status and the target charge amount of the next borehole. It is not necessary to perform a complete material suction and discharge cycle after each borehole is completed, which is conducive to improving the continuous charging efficiency. (4) By controlling the buffer through the pilot oil circuits acting on the working oil circuits on both sides of the drive power head, the hydraulic shock generated during the stopping and reversing process is depressurized and replenished. The movement speed of the reversing valve core is limited by the electro-hydraulic reversing valve buffer assembly, which can reduce the hydraulic shock and inertial displacement during intermediate stops and reverse movements, and improve the stability of the conveying process and the position control accuracy. (5) By using the ball head self-aligning transmission structure in conjunction with the sleeve rod positioning assembly, the drive power head and the lower pump body can be positioned during installation, and the axial deviation between the two can be compensated during the transmission of axial driving force, thereby reducing the adverse effects of different shafts on the piston rod assembly transmission and sealing structure. Attached Figure Description

[0017] In the attached diagram: Figure 1 This is a schematic diagram of the structure of a plunger-type delivery pump for high-viscosity emulsion explosives proposed in this invention; Figure 2 This is a cross-sectional view of the high-viscosity emulsion explosive plunger delivery pump proposed in this invention. Figure 3 The present invention proposes Figure 2 A magnified view of a section at point A in the middle; Figure 4 The present invention proposes Figure 3 View from P direction; Figure 5 This is a schematic diagram of the inlet check valve in the open state proposed in this invention; Figure 6 The present invention proposes Figure 2 A magnified view of a section at point B in the middle; Figure 7 The present invention proposes Figure 2 A magnified view of a section at point C; Figure 8This is a top view of the outlet check valve proposed in this invention; Figure 9 This is a schematic diagram of the pilot oil circuit control buffer proposed in this invention; Figure 10 This is a schematic diagram of the structure of the electro-hydraulic directional valve buffer assembly proposed in this invention; Figure 11 This is a schematic diagram of the pulse damper proposed in this invention.

[0018] In the diagram: 1-Drive power head, 2-Lower pump body, 3-Inlet check valve, 4-Delivery piston rod assembly, 5-Outlet check valve, 6-Position sensing assembly, 7-Power head valve seat, 8-Power head piston, 9-Power head cylinder, 10-Power head piston rod, 11-Power head lower end cover, 12-Sleeve positioning assembly, 13-Irregular guide ring, 14-High-pressure Glyd ring, 15-Lower pump body piston, 16-Lower pump body cylinder, 17-Cleaning port, 18-First pilot oil circuit control buffer 19-Electro-hydraulic directional valve buffer assembly, 20-Second pilot oil circuit control buffer, 21-Feed elbow, 22-Valve plate limit rod, 23-Check valve plate, 24-Inlet check valve seat, 25-Ball head rod, 26-Ball head limiting plate, 27-Ball rod seat, 28-Discharge port connector, 29-Outlet valve seat, 30-Outlet valve core, 31-Steel ball, 32-Reset spring, 33-Buffer overflow valve, 34-Replenishing oil check valve, 35-Hydraulic directional valve, 36-Throttle. Detailed Implementation

[0019] Example 1: like Figure 1 and Figure 2 As shown, this embodiment provides a high-viscosity emulsion explosive plunger-type delivery pump, including a drive power head 1, a lower pump body 2, an inlet check valve 3, a delivery piston rod assembly 4, an outlet check valve 5, a position sensing assembly 6, and a stroke buffer assembly. The drive power head 1 is located on one side of the lower pump body 2 and provides the driving force for reciprocating motion to the delivery piston rod assembly 4. One end of the delivery piston rod assembly 4 is connected to the drive power head 1, and the other end is connected to the lower pump body piston 15. The lower pump body piston 15 is slidably disposed within the lower pump body cylinder 16, thereby changing the volume of the internal storage space of the lower pump body 2 through the reciprocating motion of the lower pump body piston 15. The inlet check valve 3 is located on the feed side of the lower pump body 2, and the outlet check valve 5 is located on the discharge side of the lower pump body 2, so that the lower pump body piston 15 forms a suction and discharge process in two directions of movement, respectively.

[0020] Combination Figure 2As shown, a high-pressure Glyd ring 14 is installed in the middle of the side wall of the lower pump body piston 15, and irregularly shaped guide rings 13 are respectively embedded at the upper and lower ends of the lower pump body piston 15. The outer circumference of the irregularly shaped guide ring 13 slides in contact with the inner wall of the lower pump body cylinder 16, and is used to guide the lower pump body piston 15 radially during the reciprocating motion, reducing the possibility of piston wobble and direct metal-to-metal contact between the piston and the cylinder; the high-pressure Glyd ring 14 and the irregularly shaped guide ring 13 together form a sealing structure between the lower pump body piston 15 and the lower pump body cylinder 16. When the lower pump body piston 15 moves along the suction direction, the storage space gradually increases, and under good piston sealing conditions, a negative pressure can be formed in the storage space for sucking up high-viscosity emulsion explosives. Therefore, the lower pump body can adopt a large volume design, and the suction capacity can reach more than 6 kg at a time, and the irregularly shaped guide ring 13 and the high-pressure Glyd ring 14 enhance the guiding and sealing capabilities.

[0021] like Figures 3 to 5 As shown, the inlet check valve 3 includes an inlet check valve seat 24, a check valve plate 23, and a valve plate limiting rod 22. The inlet check valve seat 24 is provided with a feed channel connecting the feed side and the storage space. The check valve plate 23 is located on the side of the inlet check valve seat 24 facing the storage space and can move relative to the inlet check valve seat 24. The valve plate limiting rod 22 is located in the direction of movement of the check valve plate 23 away from the inlet check valve seat 24 and is used to limit the maximum opening stroke of the check valve plate 23.

[0022] During material intake, the lower pump piston 15 moves in the direction that increases the storage space, reducing the internal pressure. Under the pressure difference, the check valve plate 23 moves away from the inlet check valve seat 24, its opening displacement limited by the valve plate limiting rod 22. This creates a material channel between the check valve plate 23 and the inlet check valve seat 24, allowing the high-viscosity emulsion explosive to enter the storage space through the inlet check valve seat 24. During material discharge, the lower pump piston 15 moves in the direction that decreases the storage space, compressing the high-viscosity emulsion explosive inside the storage space and transmitting the pressure to the check valve plate 23. This causes the check valve plate 23 to re-adhere to the inlet check valve seat 24, thus closing the feed channel. This inlet valve uses a large-area valve plate that opens under negative pressure, and the valve plate limiting rod 22 limits the degree of valve plate opening, which helps maintain stable opening of the inlet check valve 3 during the intake of high-viscosity materials.

[0023] like Figure 7 and Figure 8As shown, the outlet check valve 5 includes an outlet connector 28, an outlet valve seat 29, an outlet valve core 30, a steel ball 31, and a return spring 32. The outlet valve core 30 is disposed inside the outlet valve seat 29. The outlet valve seat 29 has a lower step corresponding to the inlet of the outlet valve core 30. The side of the lower step facing the steel ball 31 forms a sealing surface adapted to the outer surface of the steel ball 31. A spring mounting groove is provided on the side of the outlet valve core 30 near the outlet. The return spring 32 is installed in the spring mounting groove. One end of the return spring 32 acts on the steel ball 31, causing the steel ball 31 to tend to move towards the lower step.

[0024] The outlet valve core 30 also has an upper step inside, which is located on the side of the steel ball 31 away from the lower step. The upper step is used to limit the maximum opening displacement of the steel ball 31 and prevent the steel ball 31 from continuing to move in the outlet direction and causing the return spring 32 to be over-compressed. The abutting part of the upper step opposite to the steel ball 31 forms a petal-shaped flow passage that is recessed towards the inside of the outlet valve core 30, so that even if the steel ball 31 moves to the upper step, it will not completely block the material passage.

[0025] Specifically, when the lower pump body 2 draws in material, a negative pressure is formed in the storage space. This negative pressure, together with the elastic force applied by the return spring 32, keeps the steel ball 31 in contact with the lower step of the outlet valve seat 29, and the outlet check valve 5 is in the closed state. During the discharge process, the high-viscosity emulsion explosive acts on the steel ball 31. When the material pressure overcomes the elastic force of the return spring 32, the steel ball 31 moves away from the lower step and compresses the return spring 32. When the steel ball 31 moves to the upper step, its continued movement is restricted, and the high-viscosity emulsion explosive enters the outlet side of the outlet valve core 30 through the petal-shaped flow passage at the upper step and is discharged through the discharge port connector 28. Thus, the outlet check valve 5 can remain closed during material intake and form a stable flow space during material discharge.

[0026] like Figure 6 As shown, a ball-head self-aligning transmission structure is used between the drive power head 1 and the conveying piston rod assembly 4. The ball-head self-aligning transmission structure includes a ball-head rod 25, a ball-head limiting plate 26, and a ball-head seat 27. One end of the ball-head rod 25 is connected to the power head piston rod 10, and the other end forms a ball head. The ball-head seat 27 has a spherical support portion on the side facing the ball-head rod 25 that is adapted to the ball head. The ball head is movably accommodated in the ball-head seat 27 and forms a spherical fit with the spherical support portion. The other end of the ball-head seat 27 is connected to the conveying piston rod assembly 4.

[0027] A ball head limiting plate 26 is disposed on the side of the ball head away from the spherical support and is connected to the cue seat 27. A limiting hole is formed on the ball head limiting plate 26 for the ball head rod 25 to pass through. The limiting hole can prevent the ball head from axially dislodging from the cue seat 27, while maintaining a certain clearance between the ball head rod 25 and the limiting hole, allowing the ball head rod 25 to swing at a small angle relative to the cue seat 27. Therefore, when the driving power head 1 transmits a large axial thrust to the lower pump body 2, even if there is a certain axial deviation between the driving power head 1 and the lower pump body 2 due to processing or installation factors, the ball head can change the force transmission angle through relative movement with the spherical surface of the cue seat 27, thereby compensating for the axial deviation between the two and reducing the lateral additional load.

[0028] Furthermore, such as Figure 2 As shown, a sleeve positioning assembly 12 is provided between the drive power head 1 and the lower pump body 2. Opposite mounting flanges are provided at the opposite ends of the drive power head 1 and the lower pump body 2, and positioning holes are formed on each of the two mounting flanges. The sleeve positioning assembly 12 includes a hollow limiting rod and a screw rod passing through the hollow limiting rod. The hollow limiting rod is positioned between the two mounting flanges, with both ends extending into the positioning holes of the two mounting flanges respectively, and restricts the radial relative movement between the drive power head 1 and the lower pump body 2 through the engagement of its outer periphery with the positioning holes; the screw rod passes through the hollow limiting rod axially and locks the two mounting flanges together, thereby restricting the axial separation of the two mounting flanges.

[0029] Therefore, the hollow limit rod mainly serves as the radial positioning element during installation, the screw mainly serves as the axial locking element after installation, and the ball-head self-aligning transmission structure is used to compensate for any remaining axial deviations that may exist after installation, forming a matching relationship between installation positioning and working self-alignment. Since the mating length between the hollow limit rod and the mounting flange can be set relatively short, after removing the screw, only a small distance needs to be moved relative to the lower pump body 2 to disengage the end of the hollow limit rod from the corresponding positioning hole, thus facilitating disassembly and maintenance.

[0030] like Figure 2 As shown, the position sensing component 6 is disposed inside the drive power head 1. In one specific embodiment, the position sensing component 6 includes a probe as a fixed detection element and a sensing ring as a moving detection element. The probe is mounted on the power head valve seat 7, and the sensing ring is mounted on the power head piston 8. When the power head piston 8 reciprocates within the power head cylinder 9 and drives the power head piston rod 10 to move, the sensing ring moves relative to the probe along with the power head piston 8. The actual movement distance of the power head piston rod 10 is obtained by detecting the relative movement between the probe and the sensing ring. Since the power head piston rod 10 is connected to the conveying piston rod assembly 4 via the aforementioned ball-head self-aligning transmission structure, this actual movement distance can characterize the actual stroke of the conveying piston rod assembly 4 and the lower pump piston 15.

[0031] With the effective working cross-sectional area of ​​the lower pump body piston 15 determined, its actual stroke corresponds to the volume change of the storage space. Therefore, the discharge process can be controlled by using the actual stroke detected by the position sensing component 6. When the amount of explosive required for the current borehole is less than the amount of material already stored in the lower pump body 2, it is not necessary for the lower pump body piston 15 to complete the entire discharge stroke. Instead, it can stop after the part of the stroke corresponding to the current amount of explosive, so that the undischarged high-viscosity emulsion explosive continues to remain in the lower pump body 2, providing a basis for continued discharge or supplementary suction in subsequent boreholes.

[0032] Furthermore, such as Figure 2 As shown, the feed end of the lower pump body 2 is provided with a feed elbow 21, which can be connected to an external feeding control component. A cleaning port 17 is provided at the bottom of the feed elbow 21. The cleaning port 17 has a detachable structure. When there are impurities or foreign objects in the inlet area, the cleaning port 17 can be opened to clean the feed elbow 21 and the vicinity of the inlet check valve 3, so as to reduce the possibility of foreign objects being stuck between the check valve plate 23 and the inlet check valve seat 24 and affecting the seal.

[0033] Furthermore, such as Figure 11 As shown, a pulse damper can also be connected to the outlet side of the outlet check valve 5. When the high-viscosity emulsion explosive passes through the pulse damper, it is first diverted by the buffer structure, then collected by the left and right rectification structures, and the fluid pressure pulse is released to the buffer air chamber through the pulse buffer membrane, thereby buffering and rectifying the flow pulsation formed by the reciprocating discharge of the plunger, making the outlet material flow more stable.

[0034] Example 2: This embodiment, based on embodiment 1, further explains the stroke buffer assembly and electro-hydraulic reversing control structure of the drive power head 1.

[0035] like Figure 2 and Figure 9 As shown, the drive power head 1 includes a power head piston 8 and a power head cylinder 9. The power head piston 8 divides the interior of the power head cylinder 9 into two hydraulic chambers located on both sides of the power head piston 8. The two hydraulic chambers are supplied with oil or discharged through a first working oil circuit and a second working oil circuit, respectively. When the first working oil circuit supplies oil to one hydraulic chamber and the second working oil circuit discharges oil from the other hydraulic chamber, the power head piston 8 moves in one direction; when the oil supply and discharge states of the two working oil circuits are exchanged, the power head piston 8 moves in the opposite direction.

[0036] The first pilot oil circuit control buffer 18 is installed in the first working oil circuit, and the second pilot oil circuit control buffer 20 is installed in the second working oil circuit. Both the first pilot oil circuit control buffer 18 and the second pilot oil circuit control buffer 20 include a buffer overflow valve 33 and a replenishing oil check valve 34. The buffer overflow valve 33 is installed in the pressure relief branch connected to the corresponding working oil circuit. When the power head piston 8 suddenly stops or reverses during its movement, the pressure in the corresponding working oil circuit rises rapidly due to the inertia of the moving parts and reaches the set pressure of the buffer overflow valve 33. The buffer overflow valve 33 then opens, allowing the working oil circuit to release the impact pressure through the pressure relief branch.

[0037] A replenishing check valve 34 is installed in the replenishing branch connected to the corresponding working oil circuit. It allows hydraulic oil to enter the corresponding working oil circuit in the replenishing direction and restricts hydraulic oil from flowing out of the working oil circuit in the opposite direction. When the corresponding working oil circuit generates a replenishing demand during the stopping or reversing process of the power head piston 8, hydraulic oil is replenished to the working oil circuit through the replenishing check valve 34. This allows the pressure relief process and the replenishing process of the working oil circuit to cooperate with each other, reducing the inertial motion of the power head piston 8 due to hydraulic shock. In one specific embodiment, the buffer relief valve 33 is a sensitive small direct-acting buffer relief valve. Its set pressure can be set to be about 5% to 10% higher than the maximum working pressure of the driving power head 1, thereby avoiding frequent pressure relief during normal operation and being able to open in time when abnormal pressure peaks occur during stopping and reversing.

[0038] like Figure 10 As shown, to further reduce the impact during power head reversal, the stroke buffer assembly also includes an electro-hydraulic directional valve buffer assembly 19. The electro-hydraulic directional valve buffer assembly 19 includes a hydraulic directional valve 35, a reversing control unit, and two throttles 36.

[0039] The hydraulic directional valve 35 is provided with an oil supply port, an oil return port, a first working port, and a second working port, wherein the first working port is connected to a first working oil circuit, and the second working port is connected to a second working oil circuit. The valve core inside the hydraulic directional valve 35 can move axially between a first reversing position and a second reversing position. When the valve core is in the first reversing position, the oil supply port is connected to the first working port, and the second working port is connected to the oil return port, thereby supplying oil to one hydraulic chamber of the power head piston 8 through the first working oil circuit and discharging oil from the other hydraulic chamber through the second working oil circuit. When the valve core is in the second reversing position, the oil supply port is connected to the second working port, and the first working port is connected to the oil return port, thereby exchanging the oil supply and discharge states of the two working oil circuits and driving the power head piston 8 to move in the opposite direction.

[0040] The valve core of the hydraulic directional valve 35 forms a first hydraulic control chamber and a second hydraulic control chamber at its two axial ends, respectively. The directional control unit is provided with a first control interface and a second control interface. The first control interface is connected to the first hydraulic control chamber via a first control oil circuit, and the second control interface is connected to the second hydraulic control chamber via a second control oil circuit. Two throttles 36 are connected in series in the first and second control oil circuits, respectively. Therefore, regardless of whether control oil enters or exits the corresponding hydraulic control chamber, its flow rate is limited by the corresponding throttle 36.

[0041] When the reversing control unit is in the first control state, the first control interface serves as the control oil inlet and the second control interface serves as the control oil return. Control oil enters the first hydraulic control chamber through the first control oil circuit and the throttle 36 in that circuit, while control oil in the second hydraulic control chamber is discharged through the second control oil circuit and the corresponding throttle 36. As the pressure in the first hydraulic control chamber builds up and the pressure in the second hydraulic control chamber is released, a hydraulic pressure difference is formed at both ends of the valve core. This hydraulic pressure difference acts on the pressure-bearing areas at both ends of the valve core, thereby pushing the valve core to move axially towards the first reversing position.

[0042] When the reversing control unit switches to another control state, the second control interface serves as the control oil inlet and the first control interface serves as the control oil return. The control oil enters the second hydraulic control chamber through the second control oil circuit and the corresponding throttle 36. At the same time, the control oil in the first hydraulic control chamber is discharged through the first control oil circuit and the corresponding throttle 36, causing the hydraulic pressure difference between the two ends of the valve core to reverse, thereby pushing the valve core to move in the opposite direction to the second reversing position.

[0043] It should be noted that the control oil entering the first or second hydraulic control chamber is mainly used to create a hydraulic pressure difference across the valve core of the hydraulic directional valve 35 and drive the valve core to move. This control oil does not continue to flow from the hydraulic control chamber into the drive power head 1 to directly push the power head piston 8. The main working hydraulic oil that actually drives the power head piston 8 is the main working hydraulic oil that enters the corresponding hydraulic chamber of the power head through the oil supply port of the hydraulic directional valve 35, the corresponding working oil port, and the first or second working oil circuit.

[0044] Therefore, the electro-hydraulic directional valve buffer assembly 19 has two interconnected hydraulic functions: the first level is that the control oil enters and exits the first and second hydraulic control chambers through the throttle 36, changes the hydraulic pressure at both ends of the valve core and controls the movement of the valve core; the second level is that the movement of the valve core changes the connection between the oil supply port, the oil return port and the first and second working oil ports, thereby switching the oil supply and discharge states of the first and second working oil circuits and ultimately changing the movement direction of the power head piston 8.

[0045] The two throttles 36 primarily function in the first-stage control process. Because the control oil entering one hydraulic control chamber and exiting from the other is restricted by throttling, the pressure build-up and release at both ends of the valve core are not instantaneous. Therefore, the movement speed of the valve core from one reversing position to another is limited. As the valve core gradually moves, the flow state of the main working oil circuit gradually switches, allowing the power head piston 8 to smoothly complete deceleration and reversal, rather than experiencing instantaneous supply and return oil switching.

[0046] The first pilot oil circuit control buffer 18, the second pilot oil circuit control buffer 20, and the electro-hydraulic directional valve buffer assembly 19 perform different but complementary functions. The first pilot oil circuit control buffer 18 and the second pilot oil circuit control buffer 20 directly act on the working oil circuits on both sides of the power head. When the power head piston 8 stops or reverses at the middle of its stroke, they relieve pressure peaks in the corresponding working oil circuits and replenish oil as needed. The electro-hydraulic directional valve buffer assembly 19 mainly reduces sudden pressure and flow changes in the main oil circuit during reversal by controlling the valve core movement speed of the hydraulic directional valve 35 when the direction of movement of the power head piston 8 needs to be changed. Therefore, when only stopping at the intermediate position, the first pilot oil circuit control buffer 18 and the second pilot oil circuit control buffer 20 can be mainly used to handle hydraulic shocks; when reversing from the intermediate position is required, the electro-hydraulic directional valve buffer assembly 19 is further used for reversal buffering.

[0047] Example 3: This embodiment, based on the plunger-type delivery pumps described in Embodiments 1 and 2, provides a method for operating a plunger-type delivery pump suitable for high-viscosity emulsion explosives used in tunnel borehole loading. This method utilizes the lower pump body 2's ability to draw in more high-viscosity emulsion explosives than required for a single borehole load in a single operation, and uses a position sensing component 6 to detect the actual stroke of the delivery piston rod assembly 4. Therefore, it eliminates the need for a complete suction and discharge stroke after each borehole is completed; instead, it can stop midway through the complete discharge stroke, retaining the remaining material, and then continue discharging or reverse suction as needed for subsequent boreholes.

[0048] Specifically, the following steps are included: S1. Material Suction and Storage: The drive head 1 drives the conveying piston rod assembly 4 to move along the suction direction. The conveying piston rod assembly 4 drives the lower pump body piston 15 to move, causing the storage space of the lower pump body 2 to gradually increase and form a negative pressure. Under the action of negative pressure, the one-way valve plate 23 of the inlet one-way valve 3 leaves the inlet one-way valve seat 24 and is limited by the valve plate limiting rod 22, thus opening the inlet one-way valve 3. At the same time, the steel ball 31 in the outlet one-way valve 5 abuts against the lower step of the outlet valve seat 29 under the combined action of negative pressure and the return spring 32, thus closing the outlet one-way valve 5. The high-viscosity emulsion explosive enters the storage space of the lower pump body 2 through the inlet one-way valve 3 via the feed elbow 21.

[0049] Preferably, the amount of material stored in a single suction operation is greater than the target charge amount for a single borehole. For example, the lower pump body 2 can suck in about 6 kg or more of material at a time, while the charge amount for a single borehole in a tunnel or horizontal tunnel can be less than this single storage amount, thereby creating conditions for completing multiple partial discharge strokes after a single storage operation.

[0050] S2. Segmented Discharge: Obtain the target charge amount for the current borehole and control the drive head 1 to move the conveying piston rod assembly 4 along the discharge direction based on the target charge amount. At this time, the lower pump piston 15 reduces the storage space, compressing the high-viscosity emulsion explosive in the storage space. Under the action of material pressure, the one-way valve plate 23 is in contact with the inlet one-way valve seat 24, and the inlet one-way valve 3 is closed. At the same time, the material pressure pushes the steel ball 31 in the outlet one-way valve 5 to overcome the elasticity of the return spring 32 and move away from the lower step, opening the outlet one-way valve 5, and the high-viscosity emulsion explosive is discharged outward through the outlet one-way valve 5.

[0051] During the discharge process, the position sensing component 6 continuously monitors the actual movement stroke of the power head piston 8 and the conveying piston rod assembly 4 connected to it. When the actual movement stroke reaches the discharge stroke corresponding to the current target charge amount in the borehole, the drive power head 1 stops moving, thereby stopping the conveying piston rod assembly 4 at the corresponding intermediate position in the complete discharge stroke. At this time, the material required for the current borehole has been discharged, while the storage space of the lower pump body 2 still retains undischarged high-viscosity emulsion explosive.

[0052] It should be noted that the middle position of the complete discharge stroke does not necessarily refer to half of the geometric length of the complete stroke, but rather to any part of the stroke stop position before the conveying piston rod assembly 4 reaches the end of the complete discharge stroke. Its specific position depends on the amount of material discharged so far.

[0053] S3. Remaining Material Judgment: After the current borehole discharge is completed, the current remaining material status is determined based on the current stopping position detected by the position sensing component 6, and the remaining material status is compared with the target charge requirement of the next borehole.

[0054] Since the effective working cross-sectional area and complete working stroke of the lower pump body piston 15 are determined, the current stopping position reflects the piston movement stroke that has been completed since the material suction position. This can characterize the current volume state of the storage space, and thus determine whether the currently retained high-viscosity emulsion explosive can meet the charging requirements of the next borehole.

[0055] When the remaining material is sufficient to meet the target charge requirements of the next borehole, the complete feeding process of refilling is not performed. Instead, step S2 is continued from the current stop position, causing the conveying piston rod assembly 4 to continue moving in the discharge direction and using the high-viscosity emulsion explosive already retained in the storage space to complete the discharge of the next borehole.

[0056] If the current remaining material is insufficient to meet the target charge requirement for the next borehole, then proceed to step S4.

[0057] S4, Intermediate Position Replenishment: The conveying piston rod assembly 4 moves directly from its current stop position in the reverse direction of material intake without first emptying the existing high-viscosity emulsion explosive in the current storage space. As the lower pump piston 15 moves in the reverse direction, the storage space expands further while retaining the original material, creating negative pressure. The inlet check valve 3 reopens, and the outlet check valve 5 closes, allowing new high-viscosity emulsion explosive to continue entering the storage space, thus achieving replenishment from the intermediate position. After replenishment is completed, the conveying piston rod assembly 4 moves in the discharge direction to perform subsequent discharge of the borehole.

[0058] When the conveying piston rod assembly 4 is stopped at the middle position of the complete discharge stroke in step S2, the first pilot oil circuit control buffer 18 and the second pilot oil circuit control buffer 20 act on the working oil circuits on both sides of the drive power head 1 to relieve pressure and replenish oil to buffer the hydraulic shock caused by the inertia of the power head piston 8 and its connected moving parts, so as to reduce the inertial displacement of the conveying piston rod assembly 4 when it passes the target stop position.

[0059] In step S4, when material is drawn from the current intermediate position in reverse, in addition to using the first pilot oil circuit control buffer 18 and the second pilot oil circuit control buffer 20 to buffer the transient pressure during the reversal process of the working oil circuit, the valve core movement speed of the hydraulic reversing valve 35 is also controlled by the electro-hydraulic reversing valve buffer assembly 19. Specifically, control oil enters the hydraulic control chamber on one side of the hydraulic reversing valve 35 through the corresponding throttle 36 and is discharged from the hydraulic control chamber on the other side through the corresponding throttle 36, so that the valve core moves from the current reversing position to another reversing position at a controlled speed; as the valve core moves, the supply and return oil relationship of the first and second working oil circuits is switched, so that the power head piston 8 smoothly changes from the original direction of movement to the opposite direction of movement. Thus, the electro-hydraulic reversing valve buffer assembly 19 is mainly used for the reverse reversal process, while the intermediate position stopping process is mainly handled by the first and second pilot oil circuit control buffers to deal with the pressure impact in the working oil circuit.

[0060] S5. Circulating Charge: After completing the discharge or replenishment of charge for the next borehole, repeat steps S2 to S4 based on the remaining material status and the target charge amount for subsequent boreholes. When the existing material in the current pump body 2 is sufficient to meet the needs of subsequent boreholes, discharge is prioritized from the current position; when the existing material is insufficient to meet the needs of subsequent boreholes, replenishment is initiated from the current position before discharge, until all boreholes in the current charge task are completed.

Claims

1. A plunger-type delivery pump for high-viscosity emulsion explosives, characterized in that: It includes a drive power head (1), a lower pump body (2), a delivery piston rod assembly (4), an inlet check valve (3), an outlet check valve (5), a position sensing assembly (6), and a stroke buffer assembly; The driving power head (1) is connected to the conveying piston rod assembly (4) in a transmission connection. One end of the conveying piston rod assembly (4) is connected to the lower pump body piston (15). The lower pump body piston (15) is slidably disposed in the lower pump body (2) so as to change the storage space of the lower pump body (2) through the reciprocating motion of the lower pump body piston (15). The inlet check valve (3) and the outlet check valve (5) are respectively located on the feed side and the discharge side of the lower pump body (2). The inlet check valve (3) includes a check valve plate (23) that opens when the storage space is under negative pressure and a limiting structure that limits the opening stroke of the check valve plate (23). The outlet check valve (5) opens when the material in the storage space is under pressure. The position sensing component (6) includes a fixed detection component and a movable detection component that moves with the power head piston (8) of the driving power head (1), and is used to detect the actual movement stroke of the conveying piston rod assembly (4) based on the relative displacement between the fixed detection component and the movable detection component. The stroke buffer assembly includes a first pilot oil circuit control buffer (18), a second pilot oil circuit control buffer (20), and an electro-hydraulic directional valve buffer assembly (19) for adjusting the reversing process of the drive power head (1). The first pilot oil circuit control buffer (18) and the second pilot oil circuit control buffer (20) act on the hydraulic oil circuits on both sides corresponding to the forward and reverse movements of the drive power head (1) to absorb hydraulic shock and balance pressure. The position sensing component (6) cooperates with the stroke buffer component to enable the conveying piston rod component (4) to stop at the middle position of the complete discharge stroke, and to continue moving in the discharge direction or in the opposite direction of the suction direction from the middle position.

2. The high-viscosity emulsion explosive plunger delivery pump according to claim 1, characterized in that: The lower pump body piston (15) has a high-pressure glyph ring (14) in the middle of its side wall. The lower and upper ends of the lower pump body piston (15) are fitted with irregular guide rings (13). The irregular guide rings (13) slide with the inner wall of the lower pump body (2). The high-pressure glyph ring (14) and the irregular guide rings (13) together maintain the sealing state of the lower pump body piston (15) during its reciprocating motion, so as to form a negative pressure for opening the inlet check valve (3) when the lower pump body piston (15) moves along the suction direction.

3. A high-viscosity emulsion explosive plunger delivery pump according to claim 2, characterized in that: The inlet check valve (3) includes an inlet check valve seat (24), a check valve plate (23), and a valve plate limiting rod (22). The inlet check valve seat (24) is provided with a feeding channel communicating with the storage space of the lower pump body (2). The check valve plate (23) is movably disposed on the side of the inlet check valve seat (24) facing the storage space and is detachably sealed with the inlet check valve seat (24). The valve plate limiting rod (22) is disposed in the opening direction of the check valve plate (23) and is used to limit the opening stroke when the check valve plate (23) is separated from the inlet check valve seat (24).

4. A high-viscosity emulsion explosive plunger delivery pump according to claim 1, characterized in that: The outlet check valve (5) includes an outlet valve seat (29), an outlet valve core (30), a steel ball (31), and a return spring (32). The outlet valve core (30) is disposed within the outlet valve seat (29). The outlet valve seat (29) has a lower step at the inlet of the outlet valve core (30), and the lower step has a sealing surface adapted to the outer surface of the steel ball (31). The outlet valve core (30) has a spring mounting groove on the side near the outlet, and the return spring (32) is disposed in the spring mounting groove and abuts against the steel ball (31). 1), so that the steel ball (31) abuts and seals with the lower step; the outlet valve core (30) is also provided with an upper step, the upper step is located on the side of the steel ball (31) away from the lower step, the upper step is used to limit the displacement of the steel ball (31) when it moves away from the lower step; the abutting part of the upper step opposite to the steel ball (31) is provided with a petal-shaped flow part that is recessed toward the inside of the outlet valve core (30), so that the steel ball (31) moves to the upper step under the action of material pressure and compresses the return spring (32).

5. A plunger-type delivery pump for high-viscosity emulsion explosives according to claim 1, characterized in that: A ball-head self-aligning transmission structure is provided between the driving power head (1) and the conveying piston rod assembly (4). The ball-head self-aligning transmission structure includes a ball-head rod (25), a ball-head limiting plate (26), and a ball-head seat (27). One end of the ball-head rod (25) is connected to the power head piston rod (10) of the driving power head (1), and the other end of the ball-head rod (25) is provided with a ball head. The ball-head seat (27) is provided with a spherical support portion adapted to the ball head. The ball head is movably accommodated in the ball-head seat (27) and forms a spherical fit with the spherical support portion. The end of the ball-head seat (27) away from the spherical support portion is connected to the conveying piston rod assembly (4). Connection; the ball head limiting plate (26) is disposed on the side of the ball head away from the spherical support and is connected to the cue seat (27). The ball head limiting plate (26) is provided with a limiting hole for the ball head rod (25) to pass through. The limiting hole is used to limit the ball head from disengaging from the cue seat (27). A movable gap is left between the ball head rod (25) and the limiting hole for the ball head rod (25) to swing relative to the cue seat (27), so that the ball head rod (25) and the cue seat (27) can compensate for the axial deviation between the drive power head (1) and the lower pump body (2) by relative swinging during the transmission of axial driving force.

6. A high-viscosity emulsion explosive plunger delivery pump according to claim 5, characterized in that: A sleeve positioning assembly (12) is provided between the drive power head (1) and the lower pump body (2). The opposite ends of the drive power head (1) and the lower pump body (2) are respectively provided with mounting flanges, and the two mounting flanges are provided with positioning holes arranged opposite to each other. The sleeve positioning assembly (12) includes a hollow limiting rod and a screw rod passing through the hollow limiting rod. The hollow limiting rod is provided between the two mounting flanges, and the two ends of the hollow limiting rod extend into the positioning holes of the two mounting flanges respectively and form a positioning fit with the corresponding positioning holes to limit the radial relative displacement between the drive power head (1) and the lower pump body (2). The screw rod passes through the hollow limiting rod along the axial direction of the hollow limiting rod and connects the two mounting flanges to limit the axial separation of the two mounting flanges. Thus, the drive power head (1) and the lower pump body (2) are installed and positioned by the cooperation of the hollow limiting rod and the two positioning holes.

7. A plunger-type delivery pump for high-viscosity emulsion explosives according to claim 1, characterized in that: The drive power head (1) has a first working oil circuit and a second working oil circuit that are respectively connected to the hydraulic chambers on both sides of the power head piston (8). The first pilot oil circuit control buffer (18) and the second pilot oil circuit control buffer (20) are respectively disposed in the first working oil circuit and the second working oil circuit. The first pilot oil circuit control buffer (18) and the second pilot oil circuit control buffer (20) each include a buffer overflow valve (33) and a replenishing oil check valve (34). The buffer overflow valve (33) is disposed on the pressure relief branch connected to the corresponding working oil circuit so as to open the pressure relief branch when the oil pressure of the corresponding working oil circuit reaches the set pressure of the buffer overflow valve (33). The replenishing oil check valve (34) is disposed on the replenishing oil branch connected to the corresponding working oil circuit. The conduction direction of the replenishing oil check valve (34) is towards the corresponding working oil circuit so as to allow hydraulic oil to enter the corresponding working oil circuit through the replenishing oil branch and restrict the hydraulic oil from flowing in the opposite direction.

8. A plunger-type delivery pump for high-viscosity emulsion explosives according to claim 7, characterized in that: The electro-hydraulic directional valve buffer assembly (19) includes a hydraulic directional valve (35), a directional control unit, and two throttles (36). The hydraulic directional valve (35) is provided with an oil supply port, an oil return port, and a first working oil port and a second working oil port respectively connected to the first working oil circuit and the second working oil circuit. The valve core of the hydraulic directional valve (35) forms a first hydraulic control chamber and a second hydraulic control chamber at its two ends. The valve core can move between a first directional position and a second directional position. When the valve core is in the first directional position, the oil supply port is connected to the first working oil port, and the second working oil port is connected to the oil return port. When the valve core is in the second directional position, the oil supply port is connected to the second working oil port, and the first working oil port is connected to the oil return port. The directional control unit is provided with a first control interface and a second control interface. The first control interface is connected to the first hydraulic control chamber through a first control oil circuit, and the second control interface is connected to the second control chamber through a second control oil circuit. The oil supply circuit is connected to the second hydraulic control chamber. The two throttles (36) are respectively connected in series in the first control oil circuit and the second control oil circuit. The reversing control unit has two control states. In one control state, the first control interface is used as the control oil inlet and the second control interface is used as the control oil return end. The control oil enters the first hydraulic control chamber through the first control oil circuit and the corresponding throttle (36), while the control oil in the second hydraulic control chamber is discharged through the second control oil circuit and the corresponding throttle (36). The valve core moves to the first reversing position. In the other control state, the first control interface is used as the control oil return end and the second control interface is used as the control oil inlet. The control oil enters the second hydraulic control chamber through the second control oil circuit and the corresponding throttle (36), while the control oil in the first hydraulic control chamber is discharged through the first control oil circuit and the corresponding throttle (36). The valve core moves to the second reversing position.

9. A method for operating a plunger-type delivery pump for high-viscosity emulsion explosives, characterized in that: The high-viscosity emulsion explosive plunger delivery pump as described in any one of claims 1-8 is operated as follows: S1: Drive the conveying piston rod assembly (4) to move along the suction direction, so that the storage space of the lower pump body (2) increases and forms a negative pressure. The inlet check valve (3) opens under the action of the negative pressure. The outlet check valve (5) relies on the weight of the steel ball (31) and the return spring (32) to provide downward elastic force to make the steel ball contact the lower step sealing surface of the outlet valve seat (29) to close the outlet check valve (5) so as to suck the high viscosity emulsion explosive into the storage space. S2: Drive the conveying piston rod assembly (4) to move along the discharge direction according to the target charge amount of the current borehole. The valve plate (23) of the inlet check valve (3) is pressed down by the hydraulic force generated by the material flow and contacts the sealing surface of the inlet check valve seat (24). The inlet check valve (3) is closed and the outlet check valve (5) is opened. The actual movement stroke of the conveying piston rod assembly (4) is detected by the position sensing assembly (6). When the actual movement stroke reaches the discharge stroke corresponding to the target charge amount of the current borehole, the conveying piston rod assembly (4) stops at the middle position of the complete discharge stroke and the undischarged high-viscosity emulsion explosive is retained in the storage space. S3: After the discharge of the current blast hole is completed, the subsequent operation mode is determined according to the remaining storage status corresponding to the current stop position of the conveying piston rod assembly (4) and the target charge amount of the next blast hole. If the remaining storage is greater than or equal to the target charge amount of the next blast hole, step S2 is executed; if the remaining storage is less than the target charge amount of the next blast hole, step S4 is executed. S4: Move the conveying piston rod assembly (4) in the opposite direction from the current stop position along the feeding direction, and replenish the feeding while retaining the high-viscosity emulsion explosive in the storage space. After the feeding is completed, execute step S5. S5: Repeat steps S2-S4 until all boreholes are loaded with explosives.

10. The working method of a high-viscosity emulsion explosive plunger delivery pump according to claim 9, characterized in that: When the conveying piston rod assembly (4) stops at the middle position of the complete discharge stroke, the hydraulic shock in the working oil circuit corresponding to the drive power head (1) is buffered by the first pilot oil circuit control buffer (18) and the second pilot oil circuit control buffer (20); when the conveying piston rod assembly (4) moves in the opposite direction of the suction direction from the middle position, the hydraulic shock generated during the reversal process of the drive power head (1) is buffered by the first pilot oil circuit control buffer (18) and the second pilot oil circuit control buffer (20), and the movement speed of the valve core of the hydraulic reversing valve (35) between the two reversing positions is limited by the throttle (36) of the electro-hydraulic reversing valve buffer assembly (19).

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