A floating cup pump using external liquid supply lubrication

Abstract

The application discloses a floating cup pump with external liquid supply lubrication, which comprises a floating cup pump body, a main shaft driving assembly, two floating cup oil delivery modules and an external liquid supply lubrication system which are installed on the floating cup pump body. An oil inlet and an oil outlet are formed in the floating cup pump body. The two floating cup oil delivery modules are symmetrically arranged in the floating cup pump body and can rotate under the driving of the main shaft driving assembly. The external liquid supply lubrication system can actively provide lubricating oil with certain pressure and flow to the matching surface friction pair between the integrated matching disc and the drum disc during the starting stage and the running process of the floating cup pump, effectively avoids the poor lubrication state caused by the insufficient oil film supporting force or the inability to match the instantaneous load change of the traditional floating cup pump which relies on the high-pressure cavity leakage oil supply, significantly reduces the wear of the friction pair, prolongs the service life of the pump and reduces the load of the motor and the power supply system.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic transmission technology, specifically relating to a float cup pump that uses external fluid supply for lubrication. Background Technology

[0002] In existing technologies, for axial piston pumps commonly found on the market, overturning moment is a significant factor limiting the number of pistons. A smaller number of pistons leads to noticeable flow and pressure pulsations. When these pulsations are transmitted to the actuator, they inevitably cause actuator vibration, periodic variations in actuator operating speed, and system noise. These problems affect the reliability and stability of the system. Therefore, auxiliary components are often added to the system's hydraulic circuit to ensure the servo system operates optimally.

[0003] For float cup pumps, since the plungers are fixedly connected to the rotor, the drum disc is not subjected to lateral forces from the plungers, resulting in almost no overturning moment. This allows for the installation of more plungers on the rotor. A greater number of plungers effectively suppresses flow and pressure pulsations, thereby increasing the stability of the hydraulic system and reducing vibration and noise. Furthermore, the plunger pair design and force balance design in its structure effectively improve the pump's operating efficiency, especially its performance at low speeds. These characteristics make it highly suitable for high-power electro-hydraulic actuators.

[0004] However, traditional float cup pumps still have some drawbacks that hinder their application in electro-hydraulic actuators. For example, there is a friction pair between the distributor plate and the drum plate. Regardless of any optimization of this friction pair, the essence is to improve the dynamic and static pressure characteristics of the oil film. However, the oil film between the friction pairs relies on leakage from the high-pressure chamber for oil supply. During the pump start-up phase, especially when starting under load, if the oil film support force has not yet been formed or cannot match the instantaneous changes in load, a poor lubrication state will occur, ultimately causing a sharp decrease in the pump's service life and also increasing the load on the motor and power supply system.

[0005] On the other hand, for traditional float cup pumps, the distribution plate is arranged on both sides, which means that the pump casing needs to have an oil passage to combine the high-pressure and low-pressure oil from both sides for output. This results in the whole machine being bulky and heavy, which is not conducive to the use of machinery with high space requirements.

[0006] In addition, as a highly integrated pump control system, the electro-hydraulic actuator in the float pump will inevitably generate heat during system operation. Due to the high degree of integration, the heat generated by the system will accumulate rapidly, causing the oil temperature to rise and ultimately reducing the viscosity of the oil in the system. Summary of the Invention

[0007] To overcome the shortcomings of existing technologies, this invention provides a float cup pump with external fluid supply lubrication, which solves the technical problems of insufficient lubrication of the friction pair between the distribution plate and the drum plate during the start-up phase, bulky pump body structure, and easy rise in oil temperature during system operation leading to a decrease in oil viscosity.

[0008] To achieve the above objectives, the specific technical solution of the present invention is as follows: An externally supplied fluid lubrication float pump includes a float pump body, a main shaft drive assembly, two float oil delivery modules, and an external fluid lubrication system mounted on the float pump body. The float pump body has an oil inlet and an oil outlet.

[0009] The two float cup oil delivery modules are symmetrically arranged inside the float cup pump body and can rotate under the drive of the main shaft drive assembly.

[0010] The float cup oil delivery module includes a roller disc, multiple float cup units, and multiple plunger units arranged sequentially from the center outwards. The roller disc is fixed at an angle to the main shaft drive assembly and can rotate synchronously with the main shaft drive assembly.

[0011] Each float cup unit is evenly distributed circumferentially on the drum. One end of each float cup unit is fixedly connected to the drum, and the other end is fitted onto the outside of the corresponding plunger unit, forming a sliding fit. This allows it to slide back and forth relative to the plunger unit when the drum rotates, and to perform oil suction and discharge processes during the reciprocating motion.

[0012] The external fluid supply lubrication system is used to supply oil to the junction between the float pump body and the drum disc.

[0013] Furthermore, the float pump body includes an integrated distribution plate and two float pump housings. The two float pump housings are respectively fixed to both ends of the integrated distribution plate. The side of the integrated distribution plate forms a distribution surface that mates with the roller disc. The roller disc fits against the distribution surface of the integrated distribution plate. An oil delivery channel communicating with an external fluid supply lubrication system is provided inside the integrated distribution plate. The oil outlet of the oil delivery channel is located on the distribution surface of the integrated distribution plate.

[0014] Furthermore, the oil inlet and outlet are respectively located on both sides of the integrated distribution plate. Each end of the integrated distribution plate has an oil inlet channel and an oil outlet channel communicating with the oil inlet and outlet, respectively. The other end of both the oil inlet and outlet channels extends to the distribution surface. An oil film supply groove is provided on the outer side of both the oil inlet and outlet channels. The end of the oil film supply groove has a damping orifice communicating with the oil outlet of the external fluid supply lubrication system.

[0015] Furthermore, the plunger unit includes a plunger body and a plunger bracket. The plunger body is fixed to the spindle drive assembly via the plunger bracket. The plunger body is divided into a ball joint section, a sliding section, and a mounting section from the outside in. An oil reservoir is provided at the outer end of the ball joint section. The sliding section has a conical structure, and its cross-sectional diameter gradually decreases from the outside in.

[0016] Furthermore, the float unit includes a float body and a float fixing pin. The float body is fixed to the roller disk by the float fixing pin. The axis of the float body is eccentrically set with respect to the axis of the float fixing pin, which is used to compensate for the axial misalignment between the float body and the plunger body caused by the tilting state of the roller disk during rotation.

[0017] Furthermore, the float cup body is cylindrical in shape, with an oil passage hole formed inside. The float cup body has an open end and a closed end. The inner edge of the closed end extends inward, forming a stepped surface that mates with the float cup fixing pin, and a positioning hole is formed in the inner ring. The float cup fixing pin passes through the oil passage hole and the positioning hole sequentially, with its tail end fitting against the stepped surface and its head end fixedly connected to the roller disc. A through hexagonal hole is formed in the center of the float cup fixing pin. Multiple oil passage grooves communicating with each hexagonal hole are formed on the roller disc.

[0018] Furthermore, the drum disc is sequentially provided with an oil delivery surface, a drum disc unloading groove, and an external fluid supply support sealing surface in the direction from the inner ring to the outer ring. Each oil groove is circumferentially distributed on the oil delivery surface. Each oil groove has an internal thread in its center, and the bottom of the float cup fixing pin has a matching external thread. The drum disc unloading groove has a ring structure, surrounding the outer side of the oil delivery surface, and is used to collect and drain oil leaking from between the float cup unit and the oil delivery surface. Unloading holes are opened around the drum disc unloading groove, connecting to the inner cavity of the float cup pump body in the float cup pump housing, for guiding oil flow into the inner cavity of the float cup pump body.

[0019] Furthermore, the external fluid supply lubrication system includes an oil injection pump and a brushless motor. The oil outlet of the oil injection pump is connected to the oil delivery channel on the integrated distribution plate. The oil inlet and outlet of the oil delivery channel are respectively connected to the inner cavity of the float pump body and the damping orifice, used to collect the oil leaking from the float pump body and output it to the distribution surface through the damping orifice. The brushless motor is used to drive the oil injection pump for oil suction and discharge operations.

[0020] Furthermore, the oil delivery channel includes an inlet concentrator pipe, an inlet pipe, and an outlet pipe. The bottom of the concentrator pipe is connected to the outlet end of the oil injection pump. One end of the inlet pipe is connected to the concentrator pipe, and the other end is connected to the mounting cavity of the float pump housing, used to collect oil leaking from the mounting cavity of the float pump housing. One end of the outlet pipe is connected to the concentrator pipe, and the other end is connected to the damping orifice on the integrated distribution plate.

[0021] Furthermore, the main shaft drive assembly includes a drive shaft, a needle roller bearing, and a bracket fixing assembly. The needle roller bearing is installed in the middle of the inner cavity of the float pump body. The drive shaft passes through the inner ring of the needle roller bearing and is interference-fitted with it. Multiple limiting strips are fixed to the outer ring of the drive shaft. Each limiting strip is evenly distributed circumferentially along the axis of the drive shaft. A limiting groove is formed between two adjacent limiting strips. Each plunger bracket is embedded in its corresponding limiting groove, thereby restricting the relative rotation between the plunger bracket and the drive shaft. The bracket fixing assembly is installed at both ends of each plunger bracket to constrain the radial degree of freedom of the plunger bracket on the drive shaft.

[0022] Compared with the prior art, the present invention has the following advantages: 1. By setting up an external fluid supply lubrication system, this invention can actively provide lubricating oil with a certain pressure and flow rate to the friction pair of the distribution surface between the integrated distribution plate and the drum plate during the start-up and operation of the float pump. This effectively avoids the poor lubrication state caused by insufficient oil film support or inability to match instantaneous load changes during the start-up phase, which is a problem in traditional float pumps that rely on high-pressure chamber leakage for oil supply. This significantly reduces the wear of the friction pair, thereby extending the service life of the pump and reducing the load on the motor and power supply system.

[0023] 2. This invention integrates the distribution plates on both sides of the traditional float pump into a central integrated distribution plate. The oil inlet, outlet, inlet channel, and outlet channel are all located within this integrated distribution plate. This simplifies the original structure, which required complex oil circuits inside the float pump housing to combine the high-pressure and low-pressure oils on both sides. It reduces the complexity of the internal oil circuits and avoids the bulky and heavy problem caused by the separate merging of high and low-pressure oils on both sides of the distribution plate. This results in a more compact float pump structure, making it suitable for applications in space-constrained machinery. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram showing the relative positions of the float cup oil delivery module and the integrated distribution plate in this invention; Figure 3 This is a schematic diagram of the integrated distribution disk in this invention; Figure 4 This is a schematic diagram showing the relative positions of the oil inlet channel, oil outlet channel, and oil film supply groove on the integrated distribution plate in this invention. Figure 5 This is a schematic diagram showing the relative positions of the oil inlet channel, the oil outlet channel, and the float cup oil delivery module in this invention; Figure 6 for Figure 2 Enlarged view of part A in the middle; Figure 7This is a schematic diagram showing the relative positions of the drum disc, the float cup unit, and the plunger unit in this invention; Figure 8 This is a schematic diagram of the structure of the plunger body in this invention; Figure 9 This is a schematic diagram of the plunger support structure in this invention; Figure 10 This is a schematic diagram of the main structure of the floating cup in this invention; Figure 11 This is a schematic diagram showing the relative positions of the oil delivery surface, the drum unloading groove, and the external liquid supply support sealing surface on the main body of the float cup in this invention; Figure 12 This is a schematic diagram of the structure of the float cup fixing pin in this invention; Figure 13 This is a schematic diagram showing the relative positions of the float cup body and the plunger body in this invention; Figure 14 This is a schematic diagram showing the center position of the float cup fixing pin and the float cup body during the movement of the present invention; Figure 15 This is a schematic diagram of the structure of the drum disc in this invention; Figure 16 This is a schematic diagram of the pipeline for the oil transport channel in this invention; Figure 17 This is a schematic diagram of the pre-tightened ball head in this invention; Figure 18 This is a schematic diagram of the structure of the roller disc connector in this invention; Figure 19 This is a schematic diagram showing the location of the screw holes in the roller disc connector of the present invention; Figure 20 This is a schematic diagram of the transmission spindle in this invention; Figure 21 This is a schematic diagram of the oil output path of the external fluid supply lubrication system in this invention.

[0025] Reference numerals: 1. Float cup pump body; 2. Main shaft drive assembly; 2-1. Transmission main shaft; 2-1-1. Limiting strip; 2-1-2. Spline; 2-1-3. Transmission shaft groove; 2-2. Needle roller bearing; 2-3. Skeleton seal ring; 2-4. Shaft snap ring; 2-5. Locking cover; 2-6. Clamp; 3. Float cup oil delivery module; 4. External fluid supply lubrication system; 5. Drum disc; 5-1. Oil passage groove; 5-2. Oil delivery surface; 5-3. Drum disc 5-4. Unloading groove; 6. External fluid supply support sealing surface; 7. Float cup unit; 8. Plunger unit; 9. Integrated distribution plate; 10. Oil inlet channel; 11. Oil outlet channel; 12. Oil drain port; 13. Plunger body; 14. Ball head section; 15. Sliding section; 16. Mounting section; 17. Plunger bracket; 18. Bracket 15-2, Piston Connection Key; 15-3, Bracket Positioning Pin Hole; 16, Float Cup Body; 16-1, Stepped Surface; 16-2, Positioning Hole; 16-3, Relief Groove; 16-4, Float Cup Bottom Sealing Surface; 16-5, Float Cup Bottom Unloading Groove; 16-6, Float Cup Bottom Auxiliary Distribution Surface; 17, Float Cup Fixing Pin; 17-1, Internal Hexagonal Hole; 17-2, Clamping Section; 17-3, Positioning Section; 18, Oil Pump; 19, Brushless Motor; 20, Temperature... 21. Pressure sensor; 22. Plug; 23. Check valve; 24. Oil delivery channel; 25. Main pipe; 26. Oil inlet pipe; 27. Oil outlet pipe; 28. Preload assembly; 29. ​​Drum disc connector; 20. Drive through hole; 21. Screw hole; 22. Preload ball head; 23. Screw guide hole; 24. Spherical protrusion; 25. Drive pin hole; 26. Drive pin; 27. Spring; 28. Screw pin. Detailed Implementation

[0026] In the description of this invention, it should be understood that the terms "one end", "the other end", "outer side", "upper side", "inner side", "horizontal", "coaxial", "center", "end", "length", "outer end", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0027] The invention will now be further described with reference to the accompanying drawings.

[0028] like Figure 1 and 2As shown, a float pump employing external fluid supply lubrication includes a float pump body 1, a main shaft drive assembly 2, two float oil delivery modules 3, and an external fluid supply lubrication system 4, all mounted on the float pump body 1. The float pump body 1 has internal mounting cavities that mate with the two float oil delivery modules 3. The two float oil delivery modules 3 are symmetrically arranged within their respective mounting cavities and can rotate under the drive of the main shaft drive assembly 2. During rotation, the two float oil delivery modules 3 can perform oil suction and discharge operations.

[0029] Specifically, the float cup oil delivery module 3 includes a roller disc 5, multiple float cup units 6, and multiple plunger units 7. The roller disc 5 is fixed at an angle to the main shaft drive assembly 2 and can rotate synchronously with the main shaft drive assembly 2. Each plunger unit 7 is evenly distributed circumferentially on the main shaft drive assembly 2, and its bottom is fixedly connected to the main shaft drive assembly 2.

[0030] Each float cup unit 6 is evenly distributed circumferentially on the drum 5. One end of each float cup unit 6 is mounted on the drum 5 and can move within a small range relative to the drum 5 to compensate for positional deviations relative to the plunger unit 7 during movement. The other end of each float cup unit 6 is sleeved on the outside of the corresponding plunger unit 7, forming a sliding fit, and can reciprocate relative to the plunger unit 7 when the drum 5 rotates, realizing the oil suction and discharge process during the reciprocating motion.

[0031] The external fluid supply lubrication system 4 is used to supply oil to the junction of the float pump body 1 and the drum 5, thereby forming an oil film on the contact surface of the two, effectively reducing friction loss.

[0032] like Figure 2 , 3 As shown in Figure 4, the float pump body 1 includes an integrated distribution plate 8 and two float pump housings 9. The two float pump housings 9 are respectively fixed at both ends of the integrated distribution plate 8. The mounting cavity is opened inside the float pump housing 9. The integrated distribution plate 8 has a conical structure with a smaller top and a larger bottom, and its side forms a distribution surface that cooperates with the roller disc 5. The roller disc 5 is attached to the distribution surface of the integrated distribution plate 8, and a distribution pair is formed between them. An oil delivery channel 23 is opened inside the integrated distribution plate 8, which is connected to the external fluid supply lubrication system 4. The oil outlet of the oil delivery channel 23 is located on the distribution surface of the integrated distribution plate 8, which can guide the oil delivered by the external fluid supply lubrication system 4 to the contact area between the roller disc 5 and the distribution surface.

[0033] like Figure 5As shown, in this embodiment, the integrated distribution plate 8 is divided into a central distribution plate body and a first support portion and a second support portion located at both ends of the distribution plate body. An oil inlet 10 and an oil outlet 11 are respectively provided on both sides of the integrated distribution plate 8. Both the first and second support portions have an oil inlet channel 8-1 and an oil outlet channel 8-2 that communicate with the oil inlet 10 and the oil outlet 11, respectively. One end of the oil inlet channel 8-1 is connected to the oil inlet 10 on the side of the integrated distribution plate 8, and the other end extends to the distribution surface, forming an oil inlet window on the distribution surface; one end of the oil outlet channel 8-2 is connected to the oil outlet 11 on the side of the integrated distribution plate 8, and the other end also extends to the distribution surface, forming an oil outlet window on the distribution surface.

[0034] During the operation of the float pump, as the drum 5 rotates with the main shaft drive assembly 2, the float unit 6 rotates circumferentially under the drive of the drum 5, and its internal volume changes with its relative position on the integrated distribution plate 8. When the float unit 6 slides to the transition area at the top, the oil chamber inside the float unit 6 closes its connection with the waist-shaped grooves on both sides (to prevent direct connection, there is a certain negative opening; the float needs to rotate a certain angle to completely cut off the connection with the oil suction area before it can connect with the oil discharge area). When the float unit 6 slides to the oil inlet window, its internal volume gradually increases, forming a negative pressure, which draws external oil into the oil inlet channel 8-1 through the oil inlet 10 and into the float unit 6 through the oil inlet window to complete the oil suction. When the float unit 6 continues to rotate to the oil discharge window, its internal volume gradually decreases, and the oil is forced into the oil discharge channel 8-2 through the oil discharge window under pressure and discharged through the oil discharge port 11, thereby achieving continuous oil transportation operation.

[0035] Furthermore, oil film supply grooves 8-3 are provided on the outer sides of both the oil inlet channel 8-1 and the oil outlet channel 8-2. A damping hole 8-4, connected to the oil outlet of the external fluid supply lubrication system 4, is provided at the end of the oil film supply groove 8-3. When the float pump is operating, the external fluid supply lubrication system 4 draws out the leaking oil from the float pump body 1 and supplies the oil through the damping hole 8-4 to the oil film supply groove 8-3 on the integrated distribution plate 8, where it is supported by the distribution surface of the integrated distribution plate 8 and the sealing strip on the outer edge of the drum disc 5.

[0036] Specifically, the external fluid supply lubrication system 4 provides oil at a constant speed and with a constant flow rate. During the external fluid supply lubrication system 4 process, the oil supply pressure depends on the side with the smaller load. The damping orifice 8-4 before entering the oil film supply tank 8-3 plays a role in balancing the load. Because the wrap angle of the oil film on both sides of the distribution channel has a phase difference, the instantaneous loads they bear cannot be the same in real time (the average load is equal), but the load difference is small. The fluid tends to flow towards the side with the lower load, resulting in more oil being supplied to the side with the lower load and less to the side with the higher load. The pressure drop of the damping orifice 8-4 increases with the increase in flow rate. Through design, the load balance on both sides can be achieved, and the oil film formed by the supply can also support the distribution plate on the side with the larger load. (The average flow rate on both sides is equal.) Furthermore, the sealing strip between the distribution surface of the integrated distribution plate 8 and the outer edge of the drum plate 5 is equivalent to a variable hydraulic resistance. The input flow of the damping orifice 8-4 must be discharged through the sealing strip. Therefore, the system pressure rises until the discharge flow of each branch is equal to the flow distributed to that branch. If the load on one side increases, a higher pressure is required to balance it. The pressure increase causes the throttling characteristics of that branch to change, and the flow is redistributed until the input flow and discharge flow are equal.

[0037] In fact, when the external load increases (the load on the oil films on both sides of the distribution channel increases simultaneously, but the ratio of the increased load on both sides remains unchanged, and the oil supply flow ratio on both sides remains unchanged), the pump's oil supply pressure increases, and the pressure distribution of the oil film also changes, increasing the thrust it can provide until the thrust is rematched with the load. When the load decreases, the pump's oil supply pressure decreases, and the thrust that the oil film can provide decreases until the thrust is rematched with the load.

[0038] In this embodiment, the float pump housing 9 adopts a housing structure with open openings at both ends. The inner side of the float pump housing 9 is fixedly connected to the integrated distribution plate 8 by bolts. A pump body end cover is fixedly provided on the outer side of the float pump housing 9 to allow for the closure or disassembly and opening of the end of the float pump housing 9. An oil drain port 12 is provided on the top surface of the float pump housing 9 to connect the inner cavity with the outside, for draining excess leaked oil.

[0039] like Figure 6 , 7As shown in Figure 8, the plunger unit 7 includes a plunger body 13, a locating pin, and a plunger bracket 15. The plunger body 13 is fixed to the plunger bracket 15 by the locating pin. The plunger body 13 is divided into a ball-end section 13-1, a sliding section 13-2, and a mounting section 13-3 from the outside in. The outer end of the ball-end section 13-1 has an oil reservoir. During the oil discharge phase, the oil pressure acts on the inner wall of the oil reservoir, causing a slight elastic deformation in the ball-end section 13-1 of the plunger body 13 to compensate for the elastic deformation caused by the oil pressure acting on the surface of the float unit 6, as well as the small gaps caused by tolerances, ensuring the normal operation of the sealing strip under high pressure conditions. The sliding section 13-2 has a conical structure, and its cross-sectional diameter gradually decreases from the outside in. The mounting section 13-3 has plunger locating pin holes and mounting grooves with mutually perpendicular axes. The top area of ​​the plunger bracket 15 is embedded in the mounting groove, forming a preliminary positioning and fixation. The positioning pin passes through the plunger bracket 15 and the plunger positioning pin hole to achieve a fixed connection between the plunger body 13 and the plunger bracket 15.

[0040] like Figure 9 As shown, in this embodiment, the plunger bracket 15 is divided into a lower bracket key 15-1 and an upper plunger connecting key 15-2. The bracket key 15-1 is a long, rod-shaped structure that is snapped into and fixed to the active drive assembly. The thickness of the plunger connecting key 15-2 matches the width of the mounting groove on the plunger body 13, allowing the mounting groove on the plunger body 13 to engage with the plunger connecting key 15-2 during installation, forming a preliminary positioning and fixation. A bracket positioning pin hole 15-3 is formed on the plunger connecting key 15-2 and coaxially arranged with the plunger positioning pin hole of the mounting section 13-3 of the plunger body 13. The positioning pin passes sequentially through the bracket positioning pin hole 15-3 of the plunger connecting key 15-2 and the plunger positioning pin hole of the mounting section 13-3 of the plunger body 13, thereby achieving a fixed connection between the plunger body 13 and the plunger bracket 15.

[0041] During the operation of the float pump, the main shaft drive assembly 2 drives the float units 6 on each plunger body 13 and the drum 5 to rotate synchronously around the axis of the main shaft drive assembly 2. Since the drum 5 is inclined, during rotation, each float unit 6 will slide axially back and forth relative to the sliding section 13-2 of the corresponding plunger body 13. When the float unit 6 slides away from the plunger body 13, the volume of the sealed cavity formed between the float unit 6 and the head of the plunger unit 7 increases, generating negative pressure. At this time, oil is drawn into the sealed cavity through the oil inlet channel 8-1 on the integrated distribution plate 8. When the float unit 6 slides closer to the plunger body 13, the volume of the sealed cavity decreases, the internal oil pressure increases, and the oil is discharged through the oil outlet channel on the integrated distribution plate 8, thus completing one oil suction and discharge cycle.

[0042] In this embodiment, each individual float cup oil delivery module 3 is provided with 16 plunger bodies 13, and the two float cup oil delivery modules 3 have a total of 32 plunger bodies 13. The plunger bodies 13 in the two float cup oil delivery modules 3 are staggered. Specifically, the plunger bodies 13 located at the same circumferential position in the two float cup oil delivery modules 3 are circumferentially separated by half a plunger body 13's distribution angle phase. This ensures that when the float cup pump is working, one plunger body 13 gradually enters the oil discharge work each time, while the other plunger body 13 gradually exits the oil discharge work. This cycle is repeated, and the 32 plunger bodies 13 can take turns entering or exiting the working range. This can effectively reduce the flow pulsation and pressure pulsation of the hydraulic pump, thereby effectively suppressing the output displacement and force fluctuations of the hydraulic system actuator and the noise caused by pulsation.

[0043] like Figure 7 , 10 As shown in Figure 11, the float unit 6 includes a float body 16 and a float fixing pin 17. The float body 16 is fixed to the roller disk 5 by the float fixing pin 17. The axis of the float body 16 is eccentrically set with respect to the axis of the float fixing pin 17, which is used to compensate for the axial offset between the float body 16 and the plunger body 13 caused by the tilting state of the roller disk 5 during rotation, and to ensure that the float body 16 and the ball head section 13-1 of the plunger unit 7 are always coaxial.

[0044] Specifically, such as Figure 13 and 14 As shown, the roller disc 5 serves as a reference plane, perpendicular to its central axis, with its center as the origin. The angle between the central axis of the roller disc and the central axis of the main shaft drive assembly is γ.

[0045] The axes of the various float cup fixing pins are evenly distributed along the circumference of the reference surface on the roller disc, with a distribution radius of R1. A line is drawn connecting the projections of the centers of the ball joints of each plunger body onto the reference surface to form a plunger trajectory circle with a radius of R2. The numerical relationship between R1 and R2 is shown in Formula 1.

[0046] like Figure 14 As shown, each float cup body arranged circumferentially on the roller disc has its axis projected onto the reference plane and undergoes circular motion around the axis of its corresponding float cup positioning pin during the rotation of the roller disc. The deviation between the axis of the float cup body and the axis of its corresponding float cup positioning pin is denoted as... ρ, ρ The calculation formula is shown in Formula 2.

[0047] During the operation of the float pump, as the drum 5 rotates, the projection of the axis of the float body 16 on the reference plane will make a circular motion around the axis of the float fixing pin 17. The displacement generated by the eccentric circular motion of the axis of the float body 16 can compensate in real time for the relative axis deviation between the float unit 6 and the plunger unit 7 caused by the tilt of the drum 5, ensuring that the inner hole axis of the float body 16 is always coaxial with the axis of the ball head section 13-1 of the plunger body 13.

[0048] Furthermore, such as Figure 10 As shown, the float cup body 16 has a cylindrical structure with an oil passage hole in its inner cavity. The float cup body 16 has an open end and a closed end. The inner edge of the closed end extends inward to form a stepped surface 16-1 that mates with the float cup fixing pin 17, and a positioning hole 16-2 is formed in the inner ring. The float cup fixing pin 17 passes through the oil passage hole and the positioning hole 16-2 in sequence and is fixedly connected to the roller disc 5. The head of the float cup fixing pin 17 has a flange that abuts against the stepped surface 16-1 of the closed end of the float cup body 16. The fixed connection between the float cup body 16 and the roller disc 5 is achieved through the engagement of the flange and the stepped surface 16-1, effectively preventing axial movement.

[0049] The float cup fixing pin 17 has a through hexagonal hole 17-1 at its center. The drum 5 has multiple oil passages 5-1 that communicate with each hexagonal hole 17-1. When the drum 5 rotates under the drive of the main shaft drive assembly 2, each oil passage 5-1 connects sequentially to the oil inlet channel 8-1 or the oil outlet channel. Through the sliding cooperation of the plunger body 13 and the float cup body 16, oil is extracted from the oil inlet channel 8-1 and discharged into the oil outlet channel.

[0050] like Figure 12 As shown, in this embodiment, the float cup fixing pin 17 is threadedly connected to the roller disc 5. The flange portion on the float cup fixing pin 17 is divided into a clamping section 17-2 and a positioning section 17-3 from top to bottom. The diameter of the clamping section 17-2 is less than or equal to the diameter of the oil passage hole on the float cup body 16, and greater than the diameter of the positioning hole 16-2. The diameter of the positioning section 17-3 is slightly smaller than the diameter of the positioning hole 16-2.

[0051] During actual installation, the positioning section 17-3 of the float cup fixing pin 17 passes sequentially through the oil passage hole and the positioning hole 16-2 at the closed end of the float cup body 16. At this time, since the diameter of the pressing section 17-2 is larger than the diameter of the positioning hole 16-2, its lower end face will tightly abut against the stepped surface 16-1 at the closed end of the float cup body 16, forming axial compression. At the same time, by utilizing the design that the diameter of the positioning section 17-3 is slightly smaller than the diameter of the positioning hole 16-2, the float cup body 16 can perform a small planar movement against the surface of the drum 5 within a certain range. This compensates for the radial error between the elliptical trajectory generated by the plunger body 13 moving relative to the drum 5 during the operation of the float cup pump and the distribution circle of the float cup body 16 on the surface of the drum 5, as well as the motion error caused by the asynchronous machining, assembly, and transmission. This ensures the smooth operation of the pump.

[0052] Furthermore, a relief groove 16-3 is provided on the inner wall of the oil passage in the float cup body 16. One end face of the relief groove 16-3 is flush with the stepped surface 16-1, which allows for sufficient space for the float cup body 16 to move relative to the float cup fixing pin 17 while facilitating finishing. This space allowance is used to accommodate the radial error between the elliptical trajectory generated by the float cup body 16 moving relative to the drum 5 during pump operation and the distribution circle of the plunger body 13 on the surface of the drum 5, as well as machining and assembly, and to provide allowance for the small radial displacement of the float cup body 16 around the float cup fixing pin 17 caused by motion errors due to asynchronous transmission.

[0053] In this embodiment, the float cup body 16 is designed using the residual clamping force method. The closed end of the float cup body 16, from the inner ring to the outer ring, is provided with a float cup bottom sealing surface 16-4, a float cup bottom unloading groove 16-5, and a float cup bottom auxiliary distribution surface 16-6. The float cup bottom unloading groove 16-5 adopts an isosceles triangular structure. When the float cup body 16 is in the oil discharge state, the bottom unloading groove 16-5 is used to remove excess pressure oil, ensuring that the oil film thrust generated by the sealing band formed by the float cup bottom sealing surface 16-4 and the surface of the roller disc 5 is within a reasonable range. This ensures good oil film lubrication in the friction pair formed by the float cup body 16 and the roller disc 5, while simultaneously pressing it tightly against the surface of the roller disc 5 to control the size of the leakage gap and thus keep the leakage within a normal range. Simultaneously, the outermost float cup bottom auxiliary support located at the bottom of the float cup body 16 increases the contact area and reduces contact stress.

[0054] like Figure 15As shown, the roller disc 5 has an oil delivery surface 5-2, an unloading groove, and an external fluid supply support sealing surface 5-4 arranged sequentially from the inner ring to the outer ring. Each oil passage groove 5-1 is circumferentially distributed on the oil delivery surface 5-2. Each oil passage groove 5-1 has an internal thread in its center, and the bottom of the float cup fixing pin 17 has an external thread that mates with it. The unloading groove of the roller disc 5 has a ring structure, surrounding the outer side of the oil delivery surface 5-2, and is used to collect and drain oil leaking from between the float cup unit 6 and the oil delivery surface 5-2. Unloading holes are opened around the unloading groove of the roller disc 5, connecting to the installation cavity in the float cup pump housing 9, to guide the oil into the cavity of the float cup pump housing 9, thus preventing leaked oil from affecting the external fluid supply lubrication system 4. The external fluid supply support sealing surface 5-4 and the oil seal supply groove on the distribution surface of the integrated distribution plate 8 form the sealing band required by the external fluid supply lubrication system 4. The sealing strip is divided into an inner sealing strip and an outer sealing strip by the oil seal supply groove. The oil output from the damping hole 8-4 in the oil seal supply groove leaks into the unloading groove through the inner sealing strip. Then it leaks into the pump casing through the outer sealing strip.

[0055] like Figure 2 and 16 As shown, the external fluid supply lubrication system 4 includes an oil injection pump 18, a brushless motor 19, a Hall sensor, and a temperature and pressure sensor 20. The oil outlet of the oil injection pump 18 is connected to the oil delivery channel 23 on the integrated distribution plate 8. The oil delivery channel 23 includes an inlet concentrator pipe 23-1, an inlet pipe 23-2, and an outlet pipe 23-3. The bottom of the concentrator pipe 23-1 is connected to the oil outlet of the oil injection pump 18. One end of the inlet pipe 23-2 is connected to the concentrator pipe 23-1, and the other end is connected to the mounting cavity of the float pump housing 9, used to collect oil leaking from the mounting cavity of the float pump housing 9. One end of the outlet pipe 23-3 is connected to the concentrator pipe 23-1, and the other end is connected to the damping hole 8-4 on the integrated distribution plate 8.

[0056] The brushless motor 19 drives the oil pump 18 for oil suction and discharge operations. Leaking oil collected from the unloading groove of the drum disc 5 and passed through the unloading hole in the mounting cavity of the float pump housing 9 is drawn into the collection pipe 23-1 via the oil inlet pipe 23-2, then transported to the damping hole 8-4 via the oil outlet pipe 23-3, and finally enters the oil film supply groove 8-3 on the integrated distribution plate 8. A Hall sensor is used to monitor the rotational speed of the brushless motor 19 in real time and feeds the speed signal back to the control system so that the oil supply flow rate of the oil pump 18 can be dynamically adjusted according to the operating status of the float pump.

[0057] In this embodiment, a one-way valve 22 is installed at the oil inlet end of the oil inlet pipe 23-2. The one-way valve 22 is used to ensure the direction of oil delivery, allowing it to flow unidirectionally from the inner cavity of the float pump housing 9, through the oil inlet pipe 23-2, into the collection pipe 23-1. Two temperature and pressure sensors 20 are installed on the integrated distribution plate 8 to collect the temperature and pressure parameters of the oil when the external fluid supply lubrication system 4 is input or output in real time.

[0058] like Figure 16 and 21 As shown, during actual operation of the float pump, the oil injection pump 18 rotates forward, drawing in the oil leaking from the various sealing surfaces of the float pump through the one-way valve 22, flowing through the inlet pipe 23-2, and finally to the collection pipe 23-1. Oil continuously accumulates in the collection pipe 23-1, gradually overflowing to the outlet pipe 23-3, and is supplied to the oil film supply groove 8-3 on the integrated distribution plate 8 through the damping orifice 8-4. The oil film support is formed by the sealing band formed by the distribution surface and the external liquid supply support sealing surface 5-4. This oil film support can be dynamically adjusted according to load changes. Simultaneously, two temperature and pressure sensors 20 measure the real-time oil temperature in the collection pipes 23-1 on both sides, adjusting the speed of the oil injection pump 18 according to the oil temperature to change the oil supply. When the oil temperature rises, increasing the speed of the oil injection pump 18 increases the oil supply, increasing the clearance between the friction pairs and thus improving lubrication. Furthermore, the leaked oil absorbs heat from the machine body, indirectly achieving a heat dissipation effect. When the oil temperature is not high, the speed of the oil injection pump 18 is reduced to save energy, and excess leaked oil is discharged through the drain port 12.

[0059] In some embodiments, a plug 21 is installed on one side of the oil inlet pipe 23-2 to seal the process hole left during the machining of the oil inlet pipe 23-2.

[0060] like Figure 20 As shown, the spindle drive assembly 2 includes a drive spindle 2-1, a needle roller bearing 2-2, and a bracket fixing assembly. The integrated distribution plate 8 has bearing mounting holes that match the needle roller bearing 2-2. The needle roller bearing 2-2 is fitted into these mounting holes, and the drive spindle 2-1 passes through the inner ring of the needle roller bearing 2-2 and is interference-fitted with it. Multiple limiting strips 2-1-1 are fixed to the outer ring of the drive spindle 2-1. Each limiting strip 2-1-1 is evenly distributed circumferentially along the axis of the drive spindle 2-1. A limiting groove is formed between adjacent limiting strips 2-1-1. Each plunger bracket 15 is embedded in its corresponding limiting groove, thereby restricting the relative rotation between the plunger bracket 15 and the drive spindle 2-1. The bracket fixing assembly is installed at both ends of each plunger bracket 15 to constrain the radial degree of freedom of the plunger bracket 15 in the transmission main shaft 2-1, prevent it from radially moving within the float pump body 1, and ensure the relative position of the plunger bracket 15 and the drum 5 is stable.

[0061] like Figure 2 and 6 As shown, the bracket fixing assembly includes a skeleton sealing ring 2-3, a shaft retaining ring 2-4, a locking cover 2-5, and a clamp 2-6. The skeleton sealing ring 2-3 is installed on the outer ring of the transmission main shaft 2-1 to achieve a seal between the pump body end cover and the transmission main shaft 2-1, preventing oil leakage from the gap between them. The plunger bracket 15 has bracket grooves at both ends that mate with the clamp 2-6. The clamp 2-6 is installed in these grooves to fix each plunger bracket 15 to the transmission shaft body. The locking cover 2-5 is fitted onto the outer ring of the clamp 2-6 to restrict its radial freedom. The shaft retaining ring 2-4 is installed on the axial outer side of the locking cover 2-5 to restrict its axial displacement.

[0062] When the float pump is working, the plunger support 15 is subjected to hydraulic pressure transmitted from the plunger body 13, which is ultimately transmitted to the clamp 2-6. Since the number of plunger bodies 13 entering the high-pressure zone is the same on both sides, the resultant force of the hydraulic force used has equal and opposite components along the axial direction. The axial component of the hydraulic force can be balanced by itself in the force system formed by the plunger support 15 and the clamp 2-6. Only the remaining radial component is transmitted to the transmission shaft 2-1. This radial component is the load that the transmission shaft 2-1 needs to overcome, and it is also the necessary component force to ensure that the pump can work normally and complete the suction and discharge operations.

[0063] In this embodiment, a spline 2-1-2 is provided at one end of the transmission spindle 2-1 for connecting the transmission spindle 2-1 to an external motor. A transmission shaft groove 2-1-3 is provided in the transmission spindle 2-1 at a position aligned with the support groove in each plunger bracket 15. An annular groove is formed between the support groove and the transmission shaft groove 2-1-3, which allows the clamp 2-6 to be inserted, providing axial and radial positioning for the clamp 2-6 when it is inserted.

[0064] Furthermore, there are four clamps 2-6 in total. The four clamps 2-6 are paired up and installed at both ends of each plunger bracket 15.

[0065] Furthermore, each plunger support 15 has a support ring groove at both ends. A support ring is installed within the support ring groove. The support ring is spaced apart from the transmission main shaft 2-1. During operation, the plunger support 15 is subjected to hydraulic pressure transmitted from the plunger body 13. This force generates a torque that acts on the plunger support 15, and the support ring and needle roller bearing 2-2 jointly bear this torque. When the deformation of the support ring is less than the gap between the support ring and the transmission main shaft 2-1 (the support ring and the transmission main shaft 2-1 do not contact each other), most of the torque on the plunger support 15 is prevented from acting on the transmission main shaft 2-1.

[0066] like Figure 7 As shown, the float pump housing 9 has a pre-tightening assembly 24 on the side facing the drum 5, which is used to tightly press the drum 5 onto the distribution surface of the integrated distribution plate 8. The pre-tightening assembly 24 includes a drum 5 connector, a pre-tightening ball head 26, multiple springs 27, and multiple screw pins 28. Each screw pin 28 is fixed on the locking cover 2-5 and is evenly distributed circumferentially along the axis of the locking cover 2-5. The spring 27 is sleeved on the outer ring of the screw pin 28, with one end abutting against the locking cover 2-5 and the other end abutting against the pre-tightening ball head 26. The pre-tightening ball head 26 abuts against the side of the drum 5 away from the integrated distribution plate 8 through the drum 5 connector, which is used to evenly transmit the pre-tightening force generated by the spring 27 to the drum 5 to overcome the pressure difference force, friction force, and centrifugal force generated when the plunger body 13 sucks oil during pump operation.

[0067] like Figure 17 As shown, in this embodiment, the tail end of the preload ball head 26 is provided with multiple screw guide holes 26-1. The head of the screw pin 28 passes through the screw pin 28 guide holes at the tail end of the preload ball head 26 to guide the spring 27. A spherical protrusion 26-2 is provided on the head end of the preload ball head 26. A ball socket matching the spherical protrusion 26-2 is provided on the roller disc 5 connector. The spherical protrusion 26-2 of the preload ball head 26 and the ball socket of the roller disc 5 connector cooperate to form a spherical pair.

[0068] Furthermore, such as Figure 17-19 As shown, the inner ring of the spherical protrusion 26-2 of the preload ball head 26 has multiple transmission keyways. Each plunger bracket 15 has a locking part on its bracket key 15-1 that mates with the transmission keyway. Each locking part is inserted into the corresponding transmission keyway, so that when the transmission spindle 2-1 rotates, the preload ball head 26 can be driven to rotate synchronously through the locking parts on each plunger bracket 15. The spherical protrusion 26-2 of the preload ball head 26 has four evenly distributed holes 26-3 for the preload ball head 26 transmission pins 26-4. Each hole 26-3 of the preload ball head 26 transmission pins 26-4 contains a transmission pin 26-4. The inner ring of the ball socket in the roller disc 5 connector has a transmission through hole 25-1 that mates with the transmission pin 26-4. The outer end of the transmission pin 26-4 is inside the transmission through hole 25-1. The surface of the roller disc 5 connector has multiple screw holes 25-2. The screw passes through the screw hole 25-2 to fix the roller disc 5 connector to the roller disc 5.

[0069] When the drive shaft 2-1 rotates under the drive of an external motor, the driving force of rotation is sequentially transmitted through the plunger bracket 15, the preload ball head 26, the transmission pin 26-4, and the roller disc 5 connector to the roller disc 5 for synchronous rotation. Simultaneously, the preload force generated by the spring 27 is transmitted to the preload ball head 26. The transmission pin 26-4 on the preload ball head 26 then transmits the power to the roller disc 5 connector, which in turn transmits the power to the roller disc 5.

[0070] The working principle of this invention is as follows: When the float pump starts, the drive shaft 2-1 begins to rotate under the drive of an external power source. The plunger bracket 15 is engaged with the limiting groove on the drive shaft 2-1, causing the plunger bracket 15 to rotate synchronously with the drive shaft 2-1. The rotation of the plunger bracket 15 drives the plunger body 13 to rotate synchronously, and the ball head section 13-1 of the plunger body 13 reciprocates within the inner hole of the float body 16 during rotation.

[0071] As the drum 5 rotates, the oil passage 5-1 on it connects sequentially with the oil inlet channel 8-1 or the oil outlet channel on the integrated distribution plate 8. When the oil passage 5-1 connects with the oil inlet channel 8-1, the plunger body 13 is in an outward sliding state, the volume of the sealed cavity formed by the float cup body 16 and the plunger body 13 increases, generating negative pressure. The oil is drawn into the oil passage 5-1 through the oil inlet channel 8-1 and enters the oil passage hole of the float cup body 16. When the oil passage 5-1 rotates to connect with the oil outlet channel, the plunger body 13 is in an inward sliding state under external action, the volume of the sealed cavity decreases, the oil is compressed and discharged through the oil passage 5-1 and the oil outlet channel, completing one oil suction and discharge cycle. During this process, the float cup bottom unloading groove 16-5 at the bottom of the float cup body 16 removes excess pressure oil when in the oil discharge state, so that a reasonable oil film counter-thrust force is formed between the float cup bottom sealing surface 16-4 and the oil delivery surface 5-2 of the drum 5, ensuring oil film lubrication and controlling leakage; the float cup bottom auxiliary distribution surface 16-6 increases the contact area and reduces the contact stress.

[0072] Simultaneously, the external fluid supply lubrication system 4 begins operation. The brushless motor 19 drives the oil injection pump 18, drawing leaked oil collected by the unloading groove of the drum disc 5 through the unloading hole into the collection pipe 23-1 via the oil inlet pipe 23-2. Oil continuously accumulates in the collection pipe 23-1, gradually overflowing into the oil outlet pipe 23-3, and is supplied through the damping hole 8-4 to the oil film supply groove 8-3 on the integrated distribution plate 8, gradually covering the distribution surface. Oil leaking at the inner sealing strip is collected by the unloading groove of the drum disc 5 and guided back into the housing cavity through the unloading hole, while oil leaking at the outer sealing strip enters the pump housing, forming a dynamic oil film support that adjusts with load changes.

[0073] Hall effect sensors monitor the speed of brushless motor 19, and temperature and pressure sensors 20 collect oil temperature and pressure parameters. The control system dynamically adjusts the speed of oil pump 18 based on these parameters: when the oil temperature rises, the speed is increased to increase the oil supply, improve lubrication and assist in heat dissipation; when the oil temperature is not high, the speed is reduced to save energy, and excess leaked oil is discharged through drain port 12.

[0074] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A float pump with externally supplied fluid lubrication, comprising a float pump body, a main shaft drive assembly mounted on the float pump body, and two float oil delivery modules, wherein the float pump body has an oil inlet and an oil outlet; the two float oil delivery modules are symmetrically arranged within the float pump body and are capable of rotating under the drive of the main shaft drive assembly, characterized in that: It also includes an external fluid supply lubrication system; The float cup oil delivery module includes a roller disc, multiple float cup units, and multiple plunger units arranged sequentially from the center outwards; the roller disc is fixed at an inclination on the main shaft drive assembly and can rotate synchronously with the main shaft drive assembly. Each float cup unit is evenly distributed on the drum disc in a circular pattern; one end of each float cup unit is fixedly connected to the drum disc, and the other end is sleeved on the outside of the corresponding plunger unit to form a sliding fit, which can slide back and forth relative to the plunger unit when the drum disc rotates, and realize the oil suction and oil discharge process during the reciprocating motion. The external fluid supply lubrication system is used to collect the oil inside the float pump body and supply oil to the junction between the float pump body and the drum disc.

2. A float cup pump with externally supplied liquid lubrication according to claim 1, characterized in that: The main body of the float pump includes an integrated distribution plate and two float pump housings; the two float pump housings are respectively fixed at both ends of the integrated distribution plate; the side of the integrated distribution plate forms a distribution surface that cooperates with the roller disc; the roller disc is attached to the distribution surface of the integrated distribution plate; an oil delivery channel connected to the external liquid supply lubrication system is opened inside the integrated distribution plate; the oil outlet of the oil delivery channel is located on the distribution surface of the integrated distribution plate.

3. A float cup pump with externally supplied liquid lubrication according to claim 2, characterized in that: The oil inlet and oil outlet are respectively located on both sides of the integrated distribution plate; the two ends of the integrated distribution plate are respectively provided with an oil inlet channel and an oil outlet channel connected to the oil inlet and oil outlet; the other end of the oil inlet channel and the oil outlet channel extends to the distribution surface; an oil film supply groove is provided on the outside of the oil inlet channel and the oil outlet channel; the end of the oil film supply groove is provided with a damping hole connected to the oil outlet of the external fluid supply lubrication system.

4. A float cup pump with externally supplied liquid lubrication according to claim 1, characterized in that: The plunger unit includes a plunger body and a plunger bracket; the plunger body is fixed to the spindle drive assembly by the plunger bracket; the plunger body is divided into a ball head section, a sliding section and an mounting section from the outside to the inside; the outer end of the ball head section is provided with an oil storage hole; the sliding section has a conical structure and the cross-sectional diameter gradually decreases from the outside to the inside.

5. A float cup pump with externally supplied liquid lubrication according to claim 1, characterized in that: The float cup unit includes a float cup body and a float cup fixing pin; the float cup body is fixed to the roller disk by the float cup fixing pin; the axis of the float cup body is eccentrically set with respect to the axis of the float cup fixing pin, which is used to compensate for the axial offset between the float cup body and the plunger body caused by the tilting state of the roller disk during rotation.

6. A float cup pump with externally supplied liquid lubrication according to claim 5, characterized in that: The float cup body is cylindrical in shape, with an oil passage hole in the inner cavity. The float cup body is divided into an open end and a closed end at both ends. The inner edge of the closed end extends inward to form a stepped surface that matches the float cup fixing pin, and the inner ring forms a positioning hole. The float cup fixing pin passes through the oil passage hole and the positioning hole in sequence, with its tail end fitting against the stepped surface and its head end fixedly connected to the roller disc. The center of the float cup fixing pin has a through hexagonal hole. The roller disc has multiple oil passage grooves that communicate with each hexagonal hole.

7. A float cup pump with externally supplied liquid lubrication according to claim 5, characterized in that: The drum disc is provided with an oil delivery surface, a drum disc unloading groove, and an external liquid supply support sealing surface in sequence from the inner ring to the outer ring. Each oil passage groove is evenly distributed circumferentially on the oil delivery surface. Each oil passage groove has an internal thread in the middle, and the bottom of the float cup fixing pin has an external thread that matches it. The drum disc unloading groove has a ring structure and surrounds the outside of the oil delivery surface. It is used to collect and discharge the oil leaking from between the float cup unit and the oil delivery surface. The drum disc unloading groove is provided with unloading holes around its perimeter that connect to the inner cavity of the float cup pump body in the float cup pump housing. These holes are used to guide the oil to the inner cavity of the float plate pump body.

8. A float cup pump with externally supplied liquid lubrication according to claim 2, characterized in that: The external fluid supply lubrication system includes an oil injection pump and a brushless motor; the oil outlet of the oil injection pump is connected to the oil delivery channel on the integrated distribution plate; the oil inlet and outlet of the oil delivery channel are respectively connected to the inner cavity of the float pump body and the damping hole, which are used to collect the oil leaking inside the float pump body and output it to the distribution surface through the damping hole; the brushless motor is used to drive the oil injection pump to perform oil suction and oil discharge operations.

9. A float cup pump with externally supplied liquid lubrication according to claim 2, characterized in that: The oil delivery channel includes an inlet concentrator pipe, an inlet oil pipe, and an outlet oil pipe; the bottom of the concentrator pipe is connected to the outlet end of the oil injection pump; one end of the inlet oil pipe is connected to the concentrator pipe, and the other end is connected to the mounting cavity of the float pump housing, for collecting oil leaked from the mounting cavity of the float pump housing; one end of the outlet oil pipe is connected to the concentrator pipe, and the other end is connected to the damping hole on the integrated distribution plate.

10. A float cup pump with external fluid lubrication according to claim 1, characterized in that: The main shaft drive assembly includes a drive shaft, a needle roller bearing, and a bracket fixing assembly. The needle roller bearing is installed in the middle of the inner cavity of the float pump body. The drive shaft passes through the inner ring of the needle roller bearing and is interference-fitted with it. Multiple limiting strips are fixed on the outer ring of the drive shaft. Each limiting strip is evenly distributed circumferentially along the axis of the drive shaft. A limiting groove is formed between two adjacent limiting strips. Each plunger bracket is embedded in its corresponding limiting groove, thereby restricting the relative rotation between the plunger bracket and the drive shaft. The bracket fixing assembly is installed at both ends of each plunger bracket to constrain the radial degree of freedom of the plunger bracket on the drive shaft.

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