Plunger flexible connection structure and reciprocating pump

Abstract

The utility model discloses a plunger flexible connecting structure and reciprocating pump, this structure is applied to the end face of plunger rod, makes plunger rod automatic alignment, this structure includes spherical surface pad, plunger buffer pad, plunger pressure cover, plunger joint and plunger locking female, reciprocating pump includes pump head, high pressure cylinder, combination valve, sleeve, plunger sleeve, plunger sleeve pressure block, locking nut, plunger, the sealing structure for reciprocating pump between locking nut and plunger, and the plunger flexible connecting structure of the end face of installation above plunger, plunger joint is connected with crankcase connecting rod, and with plunger locking female thread connection, can guarantee pre -tightening and easily detachable. Two cooperation rely on recessed groove and limit spherical surface pad spare etc. to guarantee coaxial degree and reduce eccentric wear. Spherical surface pad camber is tangent with plunger pressure cover, can automatic alignment and reduce eccentricity. Plunger buffer pad supports the buffering effect, and each component is beneficial to the efficiency and cost reduction.

Description

Technical Field

[0001] This utility model relates to the field of high-pressure pump technology, and in particular to a flexible plunger connection structure and a reciprocating pump. Background Technology

[0002] In the operation of a reciprocating pump, the coaxiality of the plunger and plunger sleeve is a core precision requirement, which directly determines whether the equipment can work stably. If the coaxiality does not meet the standard, the plunger will deviate from the preset axis during reciprocating motion, causing a series of chain problems. First, the problem of uneven wear is exacerbated. Under normal operating conditions, the two components have uniform annular contact with stable pressure. When the coaxiality deviation exceeds 0.1mm, the contact pattern changes to local point / line contact, and the local pressure suddenly rises to 3-5 times the normal level. High pressure can instantly destroy the oxide film and lubricating film on the metal surface, causing adhesive wear, resulting in peeling and scratches on the contact surface. At the same time, metal debris generated by wear is trapped in the gap, forming abrasive wear, falling into a cycle of wear-debris-more severe wear. For seals, plunger misalignment will cause excessive compression on one side and gaps on the other: excessive compression causes the elastomer of the sealing ring to age rapidly and undergo permanent deformation; gaps cause medium leakage, carrying away grease, increasing the coefficient of friction, and causing the seal life to plummet from 3000-5000 hours to 500-1000 hours, increasing the replacement frequency by 3-5 times. Secondly, the risk of structural fracture increases dramatically. Uneven wear reduces the strength of the plunger and plunger sleeve, and the misaligned plunger is subjected to lateral thrust, generating additional bending moments at stress concentration points such as the plunger rod threaded connection. When the deviation reaches 0.2mm, the stress at this location exceeds the material's yield strength by 1.2-1.5 times, easily leading to fatigue cracks over time and ultimately plunger rod fracture. Furthermore, uneven thickness after localized wear of the plunger sleeve makes weak points prone to bulging and bursting under high pressure, accompanied by media ejection and causing safety accidents. Utility Model Content

[0003] To solve the above-mentioned technical problems, another technical solution adopted by this utility model is: a flexible plunger connection structure, which is applied to the end face of the plunger rod to enable the plunger rod to automatically align; the structure includes a spherical pad 1, a plunger buffer pad 2, a plunger pressure sleeve 3, a plunger connector 4, and a plunger locking nut 5; The plunger locking nut 5 and the plunger buffer pad 2 are sequentially fitted onto the plunger rod; the plunger buffer pad 2 is located at the inner bottom surface of the plunger locking nut 5; the plunger pressure sleeve 3, the spherical pad 1 and the plunger connector 4 are sequentially pressed towards the end of the plunger rod along the axial direction of the plunger rod; the plunger pressure sleeve 3 and the spherical pad 1 are located inside the plunger connector 4. The plunger sleeve 3 is in contact with the plunger buffer pad 2, and the outer surface of the plunger connector 4 is threadedly connected to the inner surface of the plunger locking nut 5.

[0004] Furthermore, the arc surface of the spherical pad 1 is tangent to the end face of the plunger sleeve 3; when the plunger moves, the centripetal force generated by the spherical pad 1 reduces the deflection caused by gravity of the plunger rod during linear reciprocating motion, thus allowing the piston rod to automatically align.

[0005] Another technical solution adopted by this utility model is: a reciprocating pump, which includes: a pump head 6, a high-pressure cylinder 7, a combination valve 8, a sleeve 9, a plunger sleeve 10, a plunger sleeve pressure block 11, a locking nut 12, a plunger 13, a reciprocating pump sealing structure 16 located between the locking nut 12 and the plunger 13, and the above-mentioned flexible connection structure of the plunger installed on the end face of the plunger 13. The pump head 6 is connected adjacent to the high-pressure cylinder 7; The sleeve 9 and the plunger sleeve 10 are connected end to end and are both fitted inside the high-pressure cylinder 7; One end of the plunger 13 is inserted into the sleeve 9 and the plunger sleeve 10, and the plunger sleeve 10 is pressed by the plunger sleeve pressure block 11; the locking nut 12 is installed on the end face of the high pressure cylinder 7 by a locking member; The combined valve 8 is located between the pump head 6 and the sleeve 9; The liquid enters the sleeve 9 of the high-pressure cylinder 7, and the linear reciprocating motion of the plunger 13 pressurizes and stores the liquid. The liquid is then discharged after being pressurized a second time by the combination valve 8.

[0006] Furthermore, the reciprocating pump sealing structure 14 includes, from left to right, a water seal pressure ring 1401, a low-pressure sealing ring 1402, a water seal pressure ring 2 1403, and an O-ring 1404, which are sequentially fitted onto the plunger. The O-ring 1404 is fitted over the low-pressure sealing ring 1402; The water seal pressure ring 1401 and water seal pressure ring 1403 are used to seal when coolant enters between the locking nut and the plunger, to prevent coolant leakage, and to guide the movement direction of the plunger. The low-pressure sealing ring 1402 and the O-ring 1404 are used to avoid hard contact between the water seal pressure ring one 1401 and the water seal pressure ring two 1403; The sealing structure is pressed between the lock nut and the plunger of the reciprocating pump by a retaining ring 1405 through the hole.

[0007] Furthermore, the locking nut 12 is provided with a coolant inlet 15, which passes through the plunger sleeve 10; The plunger sleeve pressure block 11 is provided with several coolant branch outlets 16; The high-pressure cylinder 7 is provided with a coolant outlet 17; the plurality of coolant branch outlets 16 are connected to the coolant outlet 17; The coolant passes through the coolant inlet 15 to cool down the frictional heat generated by the linear reciprocating motion of the plunger 13, and then the coolant is discharged from the reciprocating pump through several coolant branch outlets 16 and coolant outlets 17.

[0008] Furthermore, the other end of the plunger 13 is connected to the telescopic drive component of the external device, and the plunger 13 performs linear reciprocating motion along the axis of the sleeve 9.

[0009] Furthermore, the combined valve 8 includes an inlet mechanism 801 and an outlet mechanism 802; Liquid enters the sleeve 9 through the liquid inlet mechanism 801. The linear reciprocating motion of the plunger 13 pressurizes and stores the liquid. After being pressurized twice by the liquid inlet mechanism 801, the liquid is discharged through the liquid outlet mechanism 802.

[0010] Furthermore, the liquid inlet mechanism 801 includes: The inlet valve body 8011 is installed on the inlet pipe; The inlet valve core mounting groove 8012 is located on the axis of the inlet valve body 8011; Liquid inlet valve core 8013; one end of the liquid inlet valve core 8013 is inserted into the liquid inlet valve core mounting groove 8012, and its outer edge is in contact with the inner edge of the liquid inlet valve core mounting groove 8012; the liquid inlet valve core 8013 is provided with a liquid inlet compression spring mounting groove 8014 on one end near the external pressure boosting end. The liquid inlet end cap 8015 is installed in one end of the external pressure boosting end near the liquid inlet valve body 8011; the liquid inlet end cap 8015 is provided with at least two arc-shaped through grooves 8016; The second liquid inlet compression spring mounting groove 8017 is opened on the axis of the liquid inlet end cover 8015; the first liquid inlet compression spring mounting groove 8014 and the second liquid inlet compression spring mounting groove 8017 are arranged opposite to each other and form a liquid inlet compression spring mounting space. The liquid inlet compression spring 8018 is located within the liquid inlet compression spring mounting space; At least one liquid inlet channel 8019 is provided on the liquid inlet valve body 8011 and communicates with the liquid inlet valve core mounting groove 8012; The liquid enters the inlet valve core mounting groove 8012 through the inlet channel 8019, and presses the inlet valve core 8013 against the inlet compression spring 8018, so that the inlet channel 8019 is connected to the arc-shaped through groove 8016, and the liquid enters the external pressure boosting end to complete the water intake.

[0011] Furthermore, the liquid inlet mechanism 801 also includes: a plurality of secondary pressurization channels 80110, which are opened on the axial end face of the liquid inlet valve body 8011 and are arranged in an array at a preset angle along the axis of the liquid inlet valve body 8011; When the linear reciprocating motion of the plunger 13 completes the first pressurization of the liquid, the liquid enters several secondary pressurization channels 80110 with a diameter smaller than that of the outlet of the sleeve 9, completes the second pressurization, and then enters the liquid outlet mechanism 802.

[0012] Furthermore, the liquid dispensing mechanism 802 includes: Discharge valve seat 8021, which is installed on the discharge pipe; The drain spring 8022 is installed inside the drain valve seat 8021; The outlet valve core 8023 is installed inside the drain spring 8022; When the liquid is pressurized from several secondary pressurization channels 80110 and discharged to the liquid outlet mechanism 802, the liquid presses the water outlet valve core 8023, causing the water outlet valve core 8023 to be pressed into the liquid outlet valve seat 8021, so that the liquid forms a drainage channel between the liquid outlet valve seat 8021 and the liquid inlet valve body 8011, and the liquid enters the liquid outlet pipe from the drainage channel to complete the drainage.

[0013] Compared with the prior art, the present invention has the following advantages: the plunger joint and crankcase connecting rod, the plunger locking nut and the plunger joint are connected by threads, which ensures that the connecting threads can be fully tightened when the plunger reciprocates to ensure reliable preload and maintain a good anti-loosening effect. When the connection is loosened by twisting the connecting threads in the opposite direction, the unlocking process can be completed relatively easily. It is easy to disassemble, repair and replace parts, and ensure production efficiency.

[0014] The plunger connector and the plunger locking nut cooperate with each other and have a special groove inside for pressing and limiting the spherical pad, plunger buffer pad and plunger sleeve, ensuring the coaxiality of the parts, reducing the uneven wear caused by the reciprocating motion of the plunger, and improving the service life of the plunger and plunger sleeve.

[0015] The spherical pad's arc surface is tangent to the plunger sleeve. The centripetal force generated by the movement greatly reduces the deflection caused by gravity during the plunger's reciprocating motion, allowing the piston rod to automatically align itself. This improves the coaxiality of the plunger and plunger sleeve, and largely solves problems such as plunger breakage caused by uneven plunger wear. Furthermore, the spherical pad is easy to manufacture and process, easy to replace, has a long average lifespan, is small in size, lightweight, and has good maintainability.

[0016] The plunger buffer pad is installed on the plunger and cooperates with the plunger locking nut. The elasticity of the plunger buffer pad provides support and cushioning for the plunger, which can reduce the compressive stress on the contact surface between the plunger and the plunger locking nut, extend the service life of the plunger, reduce the number of maintenance and costs, and is easy to disassemble and replace, greatly improving production efficiency and meeting social needs. Attached Figure Description

[0017] Figure 1This is a schematic diagram of the flexible plunger connection structure and reciprocating pump of this utility model.

[0018] Figure 2 This is an enlarged view of the liquid inlet mechanism of the combined valve of this utility model.

[0019] Figure 3 This is an enlarged view of the liquid outlet mechanism of the combined valve of this utility model.

[0020] Figure 4 This is a schematic diagram of the arc-shaped through groove of this utility model.

[0021] Figure 5 This is a schematic diagram of the coolant inlet and coolant branch outlet of this utility model.

[0022] Figure 6 This is a schematic diagram of the coolant inlet and coolant outlet of this utility model.

[0023] The components include: 1. Spherical pad; 2. Plunger buffer pad; 3. Plunger sleeve; 4. Plunger connector; 5. Plunger locking nut; 6. Pump head; 7. High-pressure cylinder; 801. Liquid inlet mechanism; 8010. Liquid inlet valve body; 8012. Liquid inlet valve core mounting groove; 8013. Liquid inlet valve core; 8014. Liquid inlet compression spring mounting groove one; 8015. Liquid inlet end cap; 8016. Arc-shaped through groove; 8017. Liquid inlet compression spring mounting groove two; 8018. Liquid inlet compression spring; 8019. Liquid inlet channel; 80110. Secondary... 802. Pressure boosting channel; 8021. Liquid outlet mechanism; 8022. Liquid outlet valve seat; 8023. Liquid discharge spring; 8024. Water outlet valve core; 9. Sleeve; 10. Plunger sleeve; 11. Plunger sleeve pressure block; 12. Locking nut; 13. Plunger; 14. Reciprocating pump sealing structure; 1401. Water seal pressure ring one; 1402. Low-pressure sealing ring; 1403. Water seal pressure ring two; 1404. O-ring seal; 1405. Hole retaining ring; 15. Coolant inlet; 16. Coolant branch outlet; 17. Coolant outlet. Detailed Implementation

[0024] The technical solutions of the plunger flexible connection structure provided by this utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only a part of the embodiments of this utility model, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without creative effort are within the scope of protection of this utility model.

[0025] Example 1 refer to Figure 1As shown, a flexible plunger connection structure is applied to the end face of the plunger rod to enable automatic alignment of the plunger rod. This structure includes a spherical pad 1, a plunger buffer pad 2, a plunger sleeve 3, a plunger connector 4, and a plunger locking nut 5. The plunger locking nut 5 and the plunger buffer pad 2 are sequentially fitted onto the plunger rod. The plunger buffer pad 2 is located on the inner bottom surface of the plunger locking nut 5. The plunger sleeve 3, the spherical pad 1, and the plunger connector 4 are sequentially pressed axially towards the end of the plunger rod. The plunger sleeve 3 and the spherical pad 1 are located inside the plunger connector 4. The plunger sleeve 3 is in contact with the plunger buffer pad 2, and the outer surface of the plunger connector 4 is threadedly connected to the inner surface of the plunger locking nut 5.

[0026] Specifically, the plunger locking nut 5 is the core of the entire connection structure for fixing and limiting, playing a dual crucial role. Firstly, through its inner threaded engagement with the plunger connector 4, it provides a stable assembly foundation for the entire flexible connection structure, firmly binding components such as the plunger sleeve 3, spherical pad 1, and plunger buffer pad 2 to the end face area of ​​the plunger rod, preventing loosening or detachment during plunger movement. Secondly, the internal space provides precise positioning for the plunger buffer pad 2, ensuring it stably adheres to its inner bottom surface, laying the positional foundation for subsequent buffering functions. The plunger buffer pad 2 plays a role in shock absorption and vibration mitigation, serving as a vital buffer element protecting the plunger rod and other components. It is fitted onto the plunger rod and located on the inner bottom surface of the plunger locking nut 5. When the plunger rod undergoes linear reciprocating motion, it inevitably generates some impact and vibration. At this time, the plunger buffer pad 2 utilizes the elastic properties of its material to effectively absorb this impact energy and slow down vibration transmission. Simultaneously, it can fill the tiny gap between the plunger locking nut 5 and the plunger sleeve 3, ensuring the tightness of contact between all components and preventing abnormal noises or component wear caused by gaps. The plunger sleeve 3 is a key transition component connecting the plunger buffer pad 2 and the spherical pad 1, playing a role in force transmission and guidance. One end is in close contact with the plunger buffer pad 2, and the other end is tangent to the arc surface of the spherical pad 1, which can smoothly transmit the force generated during the plunger's movement to the spherical pad 1, avoiding damage to the components caused by concentrated force transmission. In addition, the plunger sleeve 3 can also initially constrain the movement direction of the spherical pad 1, ensuring that the spherical pad 1 is always finely adjusted around the plunger rod axis, providing a stable movement basis for the subsequent automatic alignment function. The plunger sleeve 3 is a key transition component connecting the plunger buffer pad 2 and the spherical pad 1, playing a role in force transmission and guidance. One end is in close contact with the plunger buffer pad 2, and the other end is tangent to the arc surface of the spherical pad 1, which can smoothly transmit the force generated during the plunger's movement to the spherical pad 1, avoiding damage to the components caused by concentrated force transmission. In addition, the plunger sleeve 3 can also initially constrain the movement direction of the spherical pad 1, ensuring that the spherical pad 1 is always finely adjusted around the plunger rod axis, providing a stable motion basis for the subsequent automatic alignment function. The spherical pad 1 is the core component for achieving the automatic alignment function, and its unique arc-shaped structure is a key design feature. The arc surface of the spherical pad 1 is tangent to the end face of the plunger sleeve 3. This tangential fit allows the spherical pad 1 to rotate flexibly within a certain range. When the plunger rod performs linear reciprocating motion, if it deviates due to gravity, the direction of the force exerted by the plunger sleeve 3 on the spherical pad 1 will change. At this time, the arc surface of the spherical pad 1 will generate a centripetal force. This centripetal force can act in the opposite direction on the plunger rod, counteracting the deviating force caused by gravity, gradually adjusting the plunger rod back to the correct axis of motion, and ultimately achieving automatic alignment of the plunger rod, ensuring the linearity and stability of the motion.

[0027] The plunger connector 4 serves as the external connection and assembly carrier for the entire structure, primarily connecting external components and securing internal assemblies. Its outer surface is threaded into the inner surface of the plunger locking nut 5. This threaded connection not only facilitates assembly but also allows for precise control of the clamping degree of each internal component by adjusting the screw depth, ensuring appropriate contact pressure between components. This prevents instability due to excessive looseness or restricts the flexible rotation of the spherical pad 1 due to excessive tightness. Simultaneously, the internal cavity of the plunger connector 4 provides space for the plunger sleeve 3 and the spherical pad 1, ensuring orderly movement of each component within a limited space.

[0028] Furthermore, the arc surface of the spherical pad 1 is tangent to the end face of the plunger sleeve 3; when the plunger moves, the centripetal force generated by the spherical pad 1 reduces the deflection caused by gravity of the plunger rod during linear reciprocating motion, thus allowing the piston rod to automatically align.

[0029] In this embodiment, under ideal conditions, the plunger rod reciprocates linearly along its axis. At this time, the force exerted by the plunger sleeve 3 on the spherical pad 1 is aligned with the plunger rod axis, the spherical pad 1 experiences uniform force, and moves synchronously only with the plunger rod. All components are in a stable working state, with no additional skew force generated. When the plunger rod deviates from its axis during reciprocating motion due to its own weight, the direction of the plunger rod's movement changes, causing the plunger sleeve 3 to shift position. At this time, the tangential contact point between the plunger sleeve 3 and the spherical pad 1 changes, and the force exerted by the plunger sleeve 3 on the spherical pad 1 is no longer along the axis, but instead generates a tilted component force. Because the spherical pad 1 uses an arc surface design, this tilted component force is transformed into a centripetal force pointing towards the plunger rod axis under the action of the arc surface. The centripetal force generated by the spherical pad 1 acts in the opposite direction on the plunger sleeve 3, and is then transmitted to the plunger rod through the plunger sleeve 3. This centripetal force effectively counteracts the skew force caused by gravity, gradually pulling the plunger rod back to its correct trajectory. As the plunger rod continues to reciprocate, the spherical pad 1 will adjust the magnitude and direction of the centripetal force in real time according to the deflection of the plunger rod, continuously correcting the plunger rod, and finally achieving automatic alignment of the plunger rod. This ensures that the plunger rod always makes a stable linear reciprocating motion along the axis, avoiding problems such as component wear, abnormal noise, or reduced working efficiency caused by deflection. Example 2 refer to Figures 1-6 As shown, the reciprocating pump includes: a pump head 6, a high-pressure cylinder 7, a combination valve 8, a sleeve 9, a plunger sleeve 10, a plunger sleeve pressure block 11, a locking nut 12, a plunger 13, a reciprocating pump sealing structure 16 located between the locking nut 12 and the plunger 13, and a plunger flexible connection structure as described in Embodiment 1 above installed on the end face of the plunger 13. The pump head 6 is connected adjacent to the high-pressure cylinder 7. As the core interface component for liquid inlet and outlet in the reciprocating pump, the pump head 6 connects to an external liquid supply line at one end, guiding the liquid to be pressurized into the pump body; the other end is connected adjacent to the high-pressure cylinder 7, providing a transition channel for the liquid to enter the sleeve 9 inside the high-pressure cylinder 7. It also serves as the mounting carrier for the combination valve 8, ensuring a stable flow path for the liquid before and after pressurization. Simultaneously, the pump head 6 protects internal precision components such as the combination valve 8, preventing external impurities and vibrations from affecting the valve components. It also provides stable connection support for the high-pressure cylinder 7, ensuring the overall structural rigidity of the pump body.

[0030] The high-pressure cylinder 7, as the main pressure-bearing component of the reciprocating pump, internally houses components such as the sleeve 9 and plunger sleeve 10, providing a closed high-pressure space for liquid pressurization. Its high-strength material can withstand the high pressure generated by the reciprocating motion of the plunger 13, preventing deformation or damage to the cavity due to excessive pressure. The high-pressure cylinder 7 provides precise installation positioning for the sleeve 9 and plunger sleeve 10, ensuring that their axes are aligned with the movement axis of the plunger 13 after connection, preventing liquid leakage or plunger wear due to component misalignment. Simultaneously, its end face provides an installation reference for the locking nut 12, ensuring the assembly accuracy of the sealing structure.

[0031] The sleeve 9 and the plunger sleeve 10 are connected end to end and are both fitted inside the high-pressure cylinder 7. The sleeve 9, fitted inside the high-pressure cylinder 7 and connected end to end with the plunger sleeve 10, forms a closed liquid-containing space. When one end of the plunger 13 is inserted into the sleeve 9 and reciprocates, the internal volume of the sleeve 9 changes with the displacement of the plunger 13, realizing the intake, storage and initial pressurization of the liquid, and is the direct carrier for the plunger 13 to act on the liquid.

[0032] One end of the plunger 13 is inserted into the sleeve 9 and the plunger sleeve 10, and the plunger sleeve 10 is pressed by the plunger sleeve pressure block 11. The locking nut 12 is installed on the end face of the high-pressure cylinder 7 through a locking component. The sleeve 9 of the plunger sleeve 10 isolates the plunger 13 from the inner wall of the high-pressure cylinder 7, preventing the high-frequency reciprocating motion of the plunger 13 from directly wearing the high-pressure cylinder 7, and at the same time preventing the high-pressure liquid from directly contacting the inner wall of the high-pressure cylinder 7, thus extending the service life of the high-pressure cylinder 7. Moreover, the sleeve 9 can be replaced separately after wear, reducing maintenance costs. The sleeve is installed inside the high-pressure cylinder 7 and connected to the sleeve 9. Its inner wall is precisely fitted with the outer circle of the plunger 13, providing further guidance for the linear reciprocating motion of the plunger 13, ensuring the stability of the movement axis of the plunger 13 and avoiding radial offset. At the same time, it assists in sealing, reducing the leakage of high-pressure liquid in the sleeve 9 into the gap between the plunger 13 and the plunger sleeve 10, forming a double sealing guarantee with the end sealing structure. The plunger sleeve pressure block 11 fixes the plunger sleeve 10 in the high-pressure cylinder 7 through the clamping action, preventing the plunger sleeve 10 from axially displacing under the reciprocating motion of the plunger 13 or the action of liquid pressure, ensuring that the plunger sleeve 10 and the sleeve 9 always maintain a tight connection, and avoiding liquid leakage or reduced pressurization efficiency due to excessive gap between the two.

[0033] By adjusting the clamping force, the plunger sleeve pressure block 11 can compensate for the assembly dimensional errors between the plunger sleeve 10, the high-pressure cylinder 7, and the sleeve 9, ensuring that all components fit tightly and improving the overall structural stability.

[0034] The locking nut 12 is installed on the end face of the high-pressure cylinder 7 via a locking component such as a bolt. Inside the nut 12, between it and the plunger 13, are installed the aforementioned sealing structure, including a water seal ring and a low-pressure sealing ring. This provides an installation cavity for the sealing structure, and its own tightening force ensures a tight fit between the sealing structure and the end face of the plunger 13 and the high-pressure cylinder 7, preventing liquid leakage from the end of the high-pressure cylinder 7. When the plunger 13 reciprocates, the locking nut 12 indirectly limits the maximum backward displacement of the plunger 13 through the sealing structure, preventing the plunger 13 from dislodging from the sleeve 9 and the plunger sleeve 10, thus ensuring operational safety.

[0035] The isolation plunger 13, as the core moving component of the reciprocating pump, is inserted into the sleeve 9 and plunger sleeve 10 at one end and is driven by an external power source, such as a crankshaft connecting rod mechanism, to perform linear reciprocating motion. When moving forward, it compresses the liquid inside the sleeve 9, increasing the liquid pressure for initial pressurization; when moving backward, it creates a negative pressure inside the sleeve 9, drawing in the liquid to be pressurized. It is the direct power source for realizing the liquid from intake to pressurization.

[0036] The combination valve 8 is located between the pump head 6 and the sleeve 9; wherein, the liquid enters the sleeve 9 of the high-pressure cylinder 7, the linear reciprocating motion of the plunger 13 pressurizes and stores the liquid, and after the liquid is pressurized again by the combination valve 8, it is discharged through the liquid outlet mechanism 802.

[0037] The combination valve 8, located between the pump head 6 and the sleeve 9, is a key component for realizing the unidirectional flow of liquid from suction to pressurization to discharge. It typically includes a suction valve and a discharge valve. When the plunger 13 retracts and a negative pressure is created inside the sleeve 9, the suction valve opens and the discharge valve closes, guiding liquid from the pump head 6 into the sleeve 9. When the plunger 13 advances and the pressure inside the sleeve 9 increases, the suction valve closes and the discharge valve opens, delivering the initially pressurized liquid to the subsequent secondary pressurization stage. After initial pressurization by the plunger 13, the liquid needs to undergo secondary pressurization through the combination valve 8. The combination valve 8 may have a special flow channel or pressurization structure designed internally to further increase the liquid pressure, meeting the high-pressure output requirements of the reciprocating pump and ensuring that the final discharged liquid pressure meets the operating conditions.

[0038] In this embodiment, external power drives the plunger 13 to move backward and to the right along the axis, away from the pump head. At this time, the internal volume formed by the sleeve 9 and the plunger 13 gradually increases, the pressure inside the cavity decreases, and a negative pressure is formed. Under the action of the negative pressure, the suction valve of the combination valve 8 opens and the discharge valve closes. The external liquid to be pressurized enters the pump head 6 through the inlet port of the pump head 6, and then flows into the sleeve 9 through the opened suction valve until the plunger 13 retracts to its maximum stroke, filling the sleeve 9 with liquid, thus ending the suction stage. During this stage, the plunger sleeve 10 provides guidance for the retraction of the plunger 13, and the plunger sleeve pressure block 11 ensures the stability of the plunger sleeve 10 position. The end sealing structure locking nut 12 maintains a seal with the plunger 13, preventing external air from entering the sealing cavity and affecting the formation of negative pressure. After the plunger 13 retracts, the external power switches direction, driving the plunger 13 to move forward and to the left along the axis, closer to the pump head. The liquid inside the sleeve 9 is compressed by the plunger 13, the volume gradually decreases, and the liquid pressure rapidly increases, initially increasing the pressure. As the pressure inside sleeve 9 increases, the suction valve of combination valve 8 automatically closes due to the pressure difference, preventing liquid backflow to pump head 6. At this time, the liquid is temporarily stored inside sleeve 9, and the pressure continues to rise until it reaches the threshold that can open the discharge valve of combination valve 8, ending the initial pressurization stage. During this process, high-pressure cylinder 7 bears the internal high pressure, sleeve 9 isolates the liquid from high-pressure cylinder 7, and plunger sleeve 10 assists plunger 13 in stable forward movement, preventing radial displacement that could reduce pressurization efficiency. When the initially pressurized liquid pressure inside sleeve 9 reaches the opening pressure of the discharge valve of combination valve 8, the discharge valve opens, and liquid enters combination valve 8. Combination valve 8 uses internal special structures such as pressurization channels and pressure superposition chambers to perform secondary pressurization on the incoming liquid, further increasing the liquid pressure to ensure that the liquid pressure meets downstream application requirements such as high-pressure cleaning and high-pressure conveying. During the secondary pressurization process, combination valve 8 precisely controls the unidirectional flow of liquid to prevent backflow of the pressurized liquid, while pump head 6 provides stable support for combination valve 8, preventing displacement of valve components due to pressure fluctuations. The high-pressure liquid, after being pressurized twice by the combination valve 8, enters the liquid outlet mechanism 802 through the discharge channel of the combination valve 8. The liquid outlet mechanism 802 stabilizes the high-pressure liquid (if it includes a pressure stabilizing component) and transports the liquid to external pipelines or downstream equipment through an internal flow channel, completing the entire liquid pressurization and discharge process. When the plunger 13 advances to its maximum stroke, the liquid in the sleeve 9 is basically discharged, and the plunger 13 changes direction again and begins to retract, entering the next working cycle; the end sealing structure always maintains a seal to prevent high-pressure liquid from leaking between the locking nut 12 and the plunger 13, and the retaining ring in the hole ensures the stability of the sealing component position and guarantees the reliability of the seal.

[0039] Furthermore, a sealing structure for the reciprocating pump is installed between the locking nut and the plunger of the reciprocating pump for end sealing of the reciprocating pump. The structure includes, from left to right, a water seal pressure ring 1401, a low-pressure sealing ring 1402, a water seal pressure ring 1403, and an O-ring 1404, which are sequentially fitted onto the plunger.

[0040] The O-ring 1404 is fitted over the low-pressure sealing ring 1402.

[0041] The water seal ring 1401 and water seal ring 1403 are used to seal the area between the locking nut and the plunger when coolant enters, preventing coolant leakage and guiding the plunger's movement. As core components directly in contact with the coolant, water seal rings 1401 and 1403 together form the first line of defense. When coolant enters the sealing area from the gap between the locking nut and the plunger, their tight fit with the outer circumference of the plunger and the inner hole of the locking nut blocks the channel for coolant leakage to the outside of the pump body, ensuring the sealing performance of the end seal. Simultaneously, since the plunger needs to perform high-frequency reciprocating linear motion during reciprocating pump operation, the precise fit between the inner holes of water seal rings 1 and 2 and the plunger stabilizes and guides the plunger's movement, preventing seal failure or component wear due to radial displacement of the plunger and ensuring motion accuracy. The low-pressure sealing ring 1402 and O-ring 1404 are used to prevent hard contact between the first water seal ring 1401 and the second water seal ring 1403. The low-pressure sealing ring 1402 is positioned between the first water seal ring 1401 and the second water seal ring 1403, directly preventing direct rigid contact between the two metal rings. Through its own flexibility or elasticity, it absorbs the slight vibrations and impacts generated during the reciprocating motion of the plunger, reducing friction and wear between the rings and extending the overall service life of the sealing assembly. Under low-pressure conditions, it can help block a small amount of coolant seeping through the gap between the water seal rings, further improving the reliability of the sealing structure, especially suitable for low-pressure output scenarios of reciprocating pumps.

[0042] The O-ring 1404 is fitted over the low-pressure sealing ring 1402. Through its elastic deformation, it tightly conforms to the outer circumference of the low-pressure sealing ring and the inner wall of the locking nut, filling the gap between the low-pressure sealing ring and the mounting cavity. This prevents coolant from bypassing the low-pressure sealing ring and leaking out, making it an important supplement and reinforcement component to the low-pressure sealing ring. The elastic material properties of the O-ring 1404 can accommodate slight dimensional errors during the assembly of the sealing assembly, ensuring that the sealing surfaces always remain in contact and avoiding seal failure due to assembly inaccuracies.

[0043] Furthermore, the sealing structure is pressed between the locking nut and the plunger of the reciprocating pump by a retaining ring 1405. The retaining ring 1405 serves as a positioning component for the entire sealing structure. By being snapped into the inner groove of the locking nut of the reciprocating pump, it applies axial pressure from the right side to the sealing assembly composed of the water seal pressure ring 1401, low-pressure sealing ring 1402, water seal pressure ring 1403, and O-ring 1404, tightly pressing it into the sealing cavity between the locking nut and the plunger. This prevents axial displacement of the sealing assembly under the reciprocating motion of the plunger or the pressure of the coolant, ensuring the stability of the sealing structure. The retaining ring design eliminates the need for complex fastening structures to fix the sealing assembly. Subsequent maintenance only requires removing the retaining ring to remove the entire sealing assembly, improving ease of disassembly and assembly.

[0044] In this embodiment, during the assembly of the reciprocating pump, the O-ring 1404 is first fitted onto the outside of the low-pressure sealing ring 1402. Then, the water seal ring 1401, the low-pressure sealing ring 1402 with the O-ring, and the water seal ring 1403 are sequentially fitted onto the plunger from left to right, and pushed into the sealing cavity between the locking nut and the plunger. Finally, the retaining ring 1405 is installed. Through the axial clamping force of the retaining ring, all sealing components are tightly fitted: the inner hole of the water seal ring and the outer circle of the plunger, the O-ring and the low-pressure sealing ring and the inner hole of the locking nut, and the low-pressure sealing ring and the two water seal rings all form initial sealing surfaces, completing the pre-sealing state. When the reciprocating pump starts, the plunger begins to perform high-frequency reciprocating linear motion along the axis. Simultaneously, coolant may enter the sealing area from the gap between the locking nut and the plunger. At this time, the sealing structure achieves sealing and guidance according to the following logic.

[0045] The coolant entering the sealed area first contacts the water seal pressure ring 1401. The water seal pressure ring 1 blocks most of the coolant through the tight fit between its inner hole and the plunger. When a small amount of coolant continues to flow to the right, it is blocked a second time by the water seal pressure ring 1403. At the same time, the low-pressure sealing ring 1402 and the outer O-ring 1404 form a third seal, which completely prevents the coolant from bypassing the low-pressure sealing ring and leaking, ensuring that the coolant only circulates in the designated cooling channel and does not leak to the outside of the pump. During the reciprocating motion of the plunger, the water seal pressure ring 1401 and the water seal pressure ring 1403, through the precise fit between their inner holes and the plunger, always constrain the direction of the plunger's movement, preventing the plunger from shifting due to radial force, and ensuring a stable contact gap between the plunger and the sealing components. This not only ensures the accuracy of the movement but also prevents the seal from failing due to excessive gap.

[0046] When the output pressure of the reciprocating pump fluctuates, the low-pressure sealing ring 1402 can adapt to the pressure change through its own deformation, maintaining a close fit with the water seal ring; the O-ring 1404, through elastic deformation, fills the gap between the low-pressure sealing ring and the inner hole of the locking nut in real time, ensuring that the sealing surface is always effective. At the same time, the retaining ring 1405 continuously provides axial clamping force to prevent the sealing assembly from displaced due to pressure fluctuations or plunger movement, ensuring the stability and sealing performance of the entire sealing structure under different operating conditions.

[0047] Furthermore, the locking nut 12 is provided with a coolant inlet 15, which communicates with the plunger sleeve 10. The coolant inlet 15 serves as the source interface of the entire coolant system, with one end connected to an external coolant supply pipeline to receive externally supplied low-temperature coolant; the other end communicates with the plunger sleeve 10, precisely guiding the low-temperature coolant into the cooling channels inside or around the plunger sleeve 10, ensuring that the coolant can directly act on the core heat-generating area. The inlet is designed with a suitable flow channel structure to guide the coolant smoothly into the plunger sleeve 10. Simultaneously, the connection point with the plunger sleeve 10 has sealing properties and can be fitted with a sealing ring to prevent coolant leakage at the connection between the inlet and the plunger sleeve 10, ensuring efficient coolant delivery.

[0048] The plunger sleeve pressure block 11 is provided with several coolant branch outlets 16. These coolant branch outlets 16 serve as intermediate diversion nodes for coolant within the pump body. The branch outlets are evenly distributed on the plunger sleeve pressure block 11 and communicate with the cooling channels surrounding the plunger sleeve 10, allowing the high-temperature coolant, after absorbing heat, to be discharged from the area of ​​the plunger sleeve 10. The branch design increases the coolant outflow area, preventing coolant stagnation within the pump and improving heat dissipation efficiency. While achieving the coolant diversion function, it does not affect the clamping and fixing effect of the plunger sleeve pressure block 11 on the plunger sleeve 10. Through an integrated structural design, the pressure block performs both mechanical fixing and cooling channel functions, simplifying the internal structure of the pump body and reducing the number of independent components.

[0049] The high-pressure cylinder 7 is equipped with a coolant outlet 17; the plurality of coolant branch outlets 16 are connected to the coolant outlet 17. As the final outlet of the coolant system, one end is connected to the coolant branch outlet 16 on the plunger sleeve pressure block 11 to receive the high-temperature coolant discharged through the branch outlet; the other end is connected to an external coolant recovery or heat dissipation pipeline such as a radiator or cooling tower to discharge the high-temperature coolant outside the reciprocating pump, completing the coolant circulation. Integrated with the high-pressure cylinder 7, and made of the same high-strength material, it can withstand the high-pressure environment within the pump body, preventing coolant leakage from the outlet or damage to the outlet structure under high pressure, ensuring stable operation of the cooling system under high-pressure conditions of the reciprocating pump.

[0050] The coolant passes through the coolant inlet 15 to cool down the frictional heat generated by the linear reciprocating motion of the plunger 13, and then the coolant is discharged from the reciprocating pump through several coolant branch outlets 16 and coolant outlets 17.

[0051] In this embodiment, when the reciprocating pump starts and the plunger 13 begins linear reciprocating motion, the external coolant supply system starts simultaneously. The low-temperature coolant, typically water or a special cooling medium, is delivered through pipelines to the coolant inlet 15 on the locking nut 12. The coolant enters the cooling channel of the plunger sleeve 10 through the internal flow channel of the inlet 14. Since the inlet 14 is directly connected to the plunger sleeve 10, the coolant can quickly fill the flow channel around the plunger sleeve 10, forming a cooling medium layer surrounding the mating surface of the plunger 13 and the plunger sleeve 10, preparing for subsequent heat absorption. During the reciprocating motion, the outer circumference of the plunger 13 contacts and rubs against the inner wall of the plunger sleeve 10 at high frequency, generating a large amount of frictional heat, causing the temperature of the plunger 13 and the plunger sleeve 10 to rise. If the temperature is too high, it may lead to accelerated wear of components, seal failure, or even jamming. At this time, the low-temperature coolant in the flow channel of the plunger sleeve 10 is in direct contact with the inner wall of the plunger sleeve 10 and the outer circle of the plunger 13. It absorbs frictional heat through thermal conduction, keeping the temperature of the plunger 13 and plunger sleeve 10 within a safe operating range, typically not exceeding the heat resistance threshold of the component material. Simultaneously, during its flow, the coolant can indirectly carry away a small amount of heat from the sleeve 9 and the area around the high-pressure cylinder 7, helping to reduce the overall internal temperature of the pump body and improve the operational stability of each component. After absorbing frictional heat, the coolant temperature rises, becoming a high-temperature coolant. Under the action of the external supply pressure and the pressure difference in the internal flow channel, it flows from the flow channel of the plunger sleeve 10 to several coolant branch outlets 16 on the plunger sleeve pressure block 11. Because the branch outlets 15 are evenly distributed, the high-temperature coolant is diverted to multiple outlet channels, avoiding the problem of reduced flow rate and decreased heat dissipation efficiency caused by excessive flow in a single channel, ensuring that the high-temperature coolant can be quickly and evenly discharged from the plunger sleeve 10 area. The high-temperature coolant, after being diverted by the branch outlets 15, enters the coolant outlet 17 on the high-pressure cylinder 7 through the internal connecting channel. High-temperature coolant collects at outlet 16 and is then transported to a coolant heat dissipation system such as a radiator or cooling tower via an externally connected recovery pipeline. After cooling, it becomes low-temperature coolant again and is transported back to the coolant inlet 15 of the locking nut 12, forming a circulating cooling system. The entire process is synchronized with the working cycle of the reciprocating pump. As long as the plunger 13 continues to move, the coolant always circulates according to the process of introduction-heat absorption-extraction-discharge, ensuring that the frictional heat between the plunger 13 and the plunger sleeve 10 is carried away in real time, avoiding overheating that could affect the normal operation of the pump.

[0052] Furthermore, the combined valve 8 includes an inlet mechanism 801 and an outlet mechanism 802; the liquid enters the sleeve 9 through the inlet mechanism 801, and the linear reciprocating motion of the plunger 13 pressurizes and stores the liquid. After being pressurized a second time through the inlet mechanism 801, the liquid is discharged through the outlet mechanism 802.

[0053] Furthermore, the liquid inlet mechanism 801 includes an inlet valve body 8011, which is installed on the liquid inlet pipe. The inlet valve body 8011 forms the main frame of the liquid inlet mechanism 801, is installed on the liquid inlet pipe, and provides a carrier for structures such as the inlet valve core mounting groove 8012 and the inlet channel 8019, while ensuring a stable connection between the entire liquid inlet mechanism and the liquid inlet pipe to prevent liquid leakage. Through the preset position and size design of the inlet channel 8019, liquid is guided from the liquid inlet pipe into the inlet valve core mounting groove 8012, ensuring a controllable liquid flow path and laying the foundation for subsequent valve core operation.

[0054] The inlet valve core mounting groove 8012 is located on the axis of the inlet valve body 8011. The inlet valve core mounting groove 8012 provides space for the insertion and movement of the inlet valve core 8013, and through close contact with the outer edge of the inlet valve core 8013, forms a sealing structure to prevent liquid leakage from the gap between the valve core and the mounting groove during flow, ensuring effective pressure accumulation. The inlet valve core mounting groove 8012 serves as a temporary storage area after liquid entry, realizing the accumulation and transmission of liquid pressure, providing the necessary pressure environment for actuating the inlet valve core 8013.

[0055] The inlet valve core 8013 is inserted into the inlet valve core mounting groove 8012 at one end, with its outer edge contacting the inner edge of the groove. An inlet compression spring mounting groove 8014 is provided on the end of the inlet valve core 8013 near the external pressure-boosting end. The inlet valve core 8013, through its own movement and reset, enables the connection and closure of the inlet channel 8019 and the arc-shaped through groove 8016, serving as a key component for controlling the liquid flow direction and effectively preventing backflow of pressurized liquid. The inlet compression spring mounting groove 8014 on the end of the inlet valve core 8013 near the external pressure-boosting end cooperates with the inlet compression spring mounting groove 8017 on the inlet end cover 8015, providing a stable mounting space for the inlet compression spring 8018 and ensuring that the spring force is accurately transmitted to the valve core.

[0056] An inlet end cap 8015 is installed inside the external pressure boosting end near the inlet valve body 8011. The inlet end cap 8015 has at least two arc-shaped through-slots 8016. The inlet end cap 8015, installed inside the inlet valve body 8011 near the external pressure boosting end, seals the connection between the inlet mechanism 801 and the pressure boosting end, preventing liquid leakage at the junction. It also serves as a transition component between the inlet mechanism 801 and the pressure boosting end, ensuring smooth liquid flow into the pressure boosting end. Compared to traditional straight channels, the at least two arc-shaped through-slots 8016 on the end cap reduce turbulence during liquid flow, lower flow resistance, improve the efficiency of liquid entering the pressure boosting end, and ensure uniform multi-channel flow distribution.

[0057] The second liquid inlet compression spring mounting slot 8017 is located on the axis of the liquid inlet end cap 8015. The first liquid inlet compression spring mounting slot 8014 and the second liquid inlet compression spring mounting slot 8017 are arranged opposite each other, forming a liquid inlet compression spring mounting space. The liquid inlet compression spring mounting space can accurately fix the liquid inlet compression spring 8018 in the axial position, preventing the spring from shifting or tilting during compression and reset, ensuring that the spring force is transmitted along the axial direction; at the same time, it also protects the spring, preventing liquid impurities from directly contacting the spring and affecting its service life.

[0058] The inlet compression spring 8018 is located within the inlet compression spring mounting space. After water intake is complete, the inlet compression spring 8018 pushes the inlet valve core 8013 to reset through its own elastic restoring force, closing the connection between the inlet channel and the arc-shaped through groove, achieving unidirectional liquid flow control and preventing backflow; simultaneously, when the liquid pressure is insufficient, it keeps the valve core closed to prevent air from entering the inlet mechanism. When the liquid pressure fluctuates, the compression and reset of the spring acts as a buffer, preventing sudden changes in liquid pressure from impacting the valve core and end cap, thus protecting the structural stability of the components.

[0059] At least one liquid inlet channel 8019 is provided on the liquid inlet valve body 8011 and communicates with the liquid inlet valve core mounting groove 8012. Liquid enters the liquid inlet valve core mounting groove 8012 through the liquid inlet channel 8019, pressing the liquid inlet valve core 8013 against the liquid inlet compression spring 8018. This connects the liquid inlet channel 8019 with the arc-shaped through groove 8016, allowing the liquid to enter the external pressure boosting end, thus completing the water intake. The liquid inlet channel 8019 serves as the sole channel for liquid to enter the liquid inlet mechanism 801 from the liquid inlet pipe. Its number and size are designed according to the liquid flow requirements to ensure efficient and stable liquid entry into the liquid inlet valve core mounting groove 8012, forming the fundamental channel for achieving the water intake function. The uniform distribution of multiple channels ensures uniform transmission of liquid pressure within the liquid inlet valve core mounting groove 8012, guaranteeing force balance on the liquid inlet valve core 8013 and preventing valve core jamming due to uneven force. In this embodiment, the liquid inlet mechanism 801 serves as the core unit for water intake in the combined valve, achieving precise liquid introduction and unidirectional control through the linkage of various components. After the liquid flows in from the liquid inlet pipe, it first enters the liquid inlet valve core mounting groove 8012 through at least one liquid inlet channel 8019 opened on the liquid inlet valve body 8011. As the liquid continues to be injected, the amount of liquid in the liquid inlet valve core mounting groove 8012 gradually increases, and the pressure continuously accumulates, providing the power basis for driving the liquid inlet valve core 8013 to move. When the liquid pressure in the liquid inlet valve core mounting groove 8012 reaches a preset threshold, the liquid exerts an outward thrust on the liquid inlet valve core 8013. Because one end of the inlet valve core 8013 is inserted into the inlet valve core mounting groove 8012, and its outer edge is in close contact with the inner edge of the mounting groove, under the action of liquid thrust, the inlet valve core 8013 moves towards the external pressure boosting end, while simultaneously compressing the inlet compression spring 8018 located in the mounting space formed by the first inlet compression spring mounting groove 8014 and the second inlet compression spring mounting groove 8017, causing the spring to undergo compression deformation. As the inlet valve core 8013 moves, the inlet channel 8019, which was originally blocked by it, gradually aligns and connects with at least two arc-shaped through grooves 8016 on the inlet end cover 8015, forming a complete channel for liquid to flow from the inlet mechanism 801 to the external pressure boosting end. After the channel is opened, the liquid enters the inlet valve core mounting groove 8012 through the inlet channel 8019, and then flows smoothly into the external pressure boosting end connected to the inlet end cover 8015 through the connected arc-shaped through grooves 8016. When the liquid in the external booster reaches the preset storage amount, the liquid pressure on the inlet pipe side gradually decreases. Under the action of its own elastic restoring force, the inlet compression spring 8018 pushes the inlet valve core 8013 to move in the opposite direction until the inlet valve core 8013 resets and blocks the connection between the inlet channel 8019 and the arc-shaped through groove 8016 again, blocking the liquid backflow path. At this point, the water intake process is completed.

[0060] Furthermore, the liquid inlet mechanism 801 also includes: a plurality of secondary pressurization channels 80110, which are opened on the axial end face of the liquid inlet valve body 8011 and are arranged in a preset angle array along the axis of the liquid inlet valve body 8011; wherein, after the linear reciprocating motion of the plunger 13 completes the first pressurization of the liquid, the liquid enters into a plurality of secondary pressurization channels 80110 with a diameter smaller than that of the outlet of the sleeve 9, completes the second pressurization, and enters the liquid outlet mechanism 802.

[0061] Several secondary pressurization channels 80110 serve as key channels for secondary pressurization. Through a structural design where the diameter of each channel is smaller than that of the external pressurization outlet, these channels utilize Bernoulli's principle—that a smaller fluid cross-section leads to increased flow velocity and pressure—to further enhance the pressure of the liquid after primary pressurization to the target value. This meets the combined valve's requirement for high-pressure liquid discharge and is the core structure for the secondary pressurization function of the inlet mechanism 801. The secondary pressurization channels 80110 are arrayed at a preset angle along the axis of the inlet valve body 8011, evenly distributing the high-pressure liquid after primary pressurization into each channel, avoiding turbulence or excessively high local pressure caused by concentrated flow. Simultaneously, the arrayed channels guide the liquid to flow stably along the axis of the inlet valve body towards the outlet mechanism 802, reducing flow resistance and ensuring efficient discharge of the secondary pressurized liquid. The secondary pressurization channel 80110 is located on the axial end face of the inlet valve body 8011. One end communicates with the inlet valve core mounting groove 8012, and the other end directly connects to the outlet mechanism 802, forming a continuous flow channel from the primary pressurized liquid to the inlet valve core mounting groove, then to the secondary pressurization channel, and finally to the outlet mechanism. Its position design is adapted to the coaxial structure of the inlet mechanism 801 and the outlet mechanism 802, ensuring the straightness of the liquid flow path inside the entire combined valve and avoiding pressure loss caused by bends in the flow channel. In this embodiment, liquid flows in from the inlet pipe, enters the inlet valve core mounting groove 8012 through the inlet channel 8019 on the inlet valve body 8011, and the increased liquid volume causes the pressure in the groove to gradually accumulate, providing power to drive the inlet valve core 8013. When the liquid pressure in the groove reaches a preset threshold, it pushes the inlet valve core 8013 to move towards the external pressure boosting end, squeezing the inlet compression spring 8018; the inlet channel 8019 is aligned and connected with the arc-shaped through groove 8016 of the inlet end cover 8015, and the liquid flows into the external pressure boosting end through the arc-shaped through groove 8016, completing the water intake. After the liquid enters the external pressure boosting end, the pressure boosting end starts a pressure boosting program to initially pressurize the liquid; when the first pressure boosting is completed, the high-pressure liquid in the pressure boosting end has the power to flow towards the outlet mechanism 802. At this time, the inlet compression spring 8018 is still in a compressed state, and the inlet valve core 8013 is not fully reset, leaving a channel for the liquid to flow back through the inlet mechanism 801. After initial pressurization, the liquid flows back along the original path into the inlet mechanism 801. It first flows through the arc-shaped groove 8016 of the inlet end cap 8015 and enters the inlet valve core mounting groove 8012. Since several secondary pressurization grooves 80110 are opened on the axial end face of the inlet valve body 8011, the high-pressure liquid enters these smaller-diameter secondary pressurization grooves 80110 under pressure. According to the principle of fluid mechanics, when the liquid flows through the narrowed channel, the flow velocity increases and the pressure further increases, thus completing the second pressurization. The liquid after secondary pressurization directly enters the outlet mechanism 802 through the secondary pressurization grooves 80110 and is finally discharged by the outlet mechanism 802, thus completing the entire pressurization and flow guiding process of the inlet mechanism.

[0062] Furthermore, the liquid dispensing mechanism 802 includes: The outlet valve seat 8021 is installed on the outlet pipe. As the main frame of the outlet mechanism 802, the outlet valve seat 8021 provides a stable mounting space for the discharge spring 8022 and the outlet valve core 8023, while ensuring a sealed connection between the outlet mechanism and the outlet pipe to prevent liquid leakage during the discharge process. Through its structural cooperation with the inlet valve body 8011, a discharge channel is formed between the two when the outlet valve core 8023 moves inward, providing a transition path for the secondary pressurized liquid from the inlet mechanism 801 to the outlet pipe, ensuring controllable liquid flow direction.

[0063] The drain spring 8022 is installed inside the outlet valve seat 8021. When the liquid pressure is insufficient, its own elastic restoring force pushes the outlet valve core 8023 to reset, blocking the drain channel and preventing liquid in the outlet pipe from flowing back to the inlet mechanism 801 or the external booster end, thus ensuring stable internal pressure of the combination valve. The spring force of the drain spring 8022 is preset to match the liquid pressure after secondary pressurization. Only when the liquid pressure is greater than the spring force can it push the outlet valve core 8023 to move and open the drain channel, indirectly screening the discharged liquid pressure to ensure that only liquid reaching the preset pressure can be discharged, meeting the pressure requirements of the user.

[0064] The outlet valve core 8023 is installed inside the drain spring 8022. Through the action of being pushed inward by liquid pressure to open the channel, and then pushed back to close the channel by spring force, it achieves precise opening and closing of the drain channel. It is a key component for controlling the timing of liquid discharge and effectively prevents liquid backflow. Installed inside the drain spring 8022, it provides axial positioning for the drain spring 8022, preventing the spring from shifting or tilting during compression and reset, ensuring that the spring force is evenly transmitted to the valve core along the axial direction, and guaranteeing stable and smooth valve core operation.

[0065] When the liquid is pressurized from several secondary pressurization channels 1010 and discharged to the liquid outlet mechanism 802, the liquid presses the water outlet valve core 8023, causing the water outlet valve core 8023 to be pressed into the liquid outlet valve seat 8021, so that the liquid forms a drainage channel between the liquid outlet valve seat 8021 and the liquid inlet valve body 8011, and the liquid enters the liquid outlet pipe from the drainage channel to complete the drainage.

[0066] In this embodiment, the liquid undergoes its first pressurization at the pressurization end, while the inlet compression spring 8018 is not fully reset, reserving a channel for reverse liquid flow. The liquid, after the first pressurization, flows back into the inlet valve core mounting groove 8012, undergoes a second pressurization through the smaller-diameter secondary pressurization channel 80110, and then flows to the outlet mechanism 802. The high-pressure liquid after the second pressurization enters the outlet mechanism 802, first acting on the outlet valve core 8023. The liquid pressure is greater than the elastic force of the drain spring 8022 inside the outlet valve seat 8021, pushing the outlet valve core 8023 towards the interior of the outlet valve seat 8021, while simultaneously compressing the drain spring 8022. As the outlet valve core 8023 moves inward, a gap is formed between the outlet valve seat 8021 and the inlet valve body 801, which was originally blocked by the outlet valve core 8023; this gap forms the drain channel. After secondary pressurization, the liquid enters the outlet valve seat 8021 through the drain channel, and then flows into the outlet pipe connected to the outlet valve seat 8021, finally completing the drainage. When the liquid is discharged to the preset amount or the pressure at the external pressurization end decreases, the thrust of the liquid on the outlet valve core 8023 is less than the elastic restoring force of the drain spring 8022. The drain spring 8022 pushes the outlet valve core 8023 to reset, re-sealing the gap between the outlet valve seat 8021 and the inlet valve body 801, closing the drain channel, preventing the liquid from flowing back into the outlet pipe, and the combination valve waits for the next working cycle.

[0067] The above description details one embodiment of the present utility model, but it is merely a preferred embodiment and should not be construed as limiting the scope of the present utility model. All equivalent variations and improvements made within the scope of the present utility model application should still fall within the patent coverage of the present utility model.

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