An axial piston pump with a streamlined plunger system and a method of operation thereof

Abstract

An axial plunger pump with a streamlined plunger system and a working method thereof belong to the technical field of hydraulic transmission. A center transmission shaft is arranged in a shell, and an outer side has a guide swing angle plate, a rotary disc, a plunger cylinder body and an oil distribution plate. The guide swing angle plate and the oil distribution plate are fixed with the shell, the inclined surface of the guide swing angle plate is attached to the rotary disc, the plunger cylinder body is fixed with the center transmission shaft, the end surface adjacent to the rotary disc has a plunger groove, the plunger groove and a plunger rod reciprocate slidingly, the plunger rod is hinged with a sliding shoe ball, the sliding shoe is fixed with the rotary disc; the axis of the plunger rod is parallel to the axis of the center transmission shaft; the other end of the plunger cylinder body is attached to the oil distribution plate, the plunger groove has an oil passage communicated with the oil distribution plate, the end of the shell is fixed with an end cover, the end cover is provided with an oil inlet communicated with the oil distribution plate and an oil outlet. The present application realizes efficient suction, pressurization and discharge of hydraulic oil, meets the power demand of the hydraulic system, has wide adaptability, wide application prospect and significant economic benefits.

Description

Technical Field

[0001] This invention relates to an axial piston pump with a streamlined piston system and its operating method, belonging to the field of hydraulic transmission technology. Background Technology

[0002] Hydraulic transmission is widely used in industrial fields. As a key core power component of hydraulic systems, the performance of axial piston pumps plays a decisive role in the efficiency of the entire hydraulic system. Therefore, improving the performance of axial piston pumps has a positive and far-reaching significance for enhancing the performance of the entire hydraulic system.

[0003] Traditional axial piston pump systems typically feature simple cylindrical or other conventional shapes, which presents several drawbacks in actual operation. For instance, the piston rod and piston groove in traditional axial piston pumps are often designed with simple cylindrical shapes, resulting in a large contact area during reciprocating motion and significant frictional resistance. This not only increases energy loss and reduces the efficiency of the axial piston pump but may also lead to oil overheating.

[0004] Secondly, when an axial piston pump operates under high pressure, the uneven force distribution between the piston rod and piston groove can easily lead to localized stress concentration. This uneven stress accelerates component wear, reduces the surface quality and fitting accuracy of components, and may even cause component damage, severely shortening the pump's service life and increasing equipment maintenance costs and downtime. This, in turn, reduces pump efficiency, affecting the service life of the piston system and the overall performance of the piston pump.

[0005] Furthermore, traditional axial piston pumps are prone to cavitation during the oil suction process. This is because the traditional design of the piston rod results in poor oil flow in the suction area, easily creating negative pressure and causing gas in the oil to precipitate and form bubbles. When these bubbles enter the high-pressure area, they rapidly burst under high pressure, generating high-frequency shock waves that cause noise and vibration. This cavitation phenomenon not only damages the pump's internal components but can also lead to oil contamination, affecting the stability and reliability of the entire hydraulic system. Especially in applications sensitive to noise and vibration, it severely interferes with the normal operation of the equipment. Summary of the Invention

[0006] To address the problems existing in the background art, the present invention provides an axial piston pump with a streamlined piston system and its operating method.

[0007] To achieve the above objectives, the present invention adopts the following technical solution: an axial piston pump with a streamlined piston system, comprising a housing, a guide vane, a central drive shaft, a distributor plate, a piston cylinder, a rotary disc, a slipper, a piston rod, and an end cap; the output end of the central drive shaft is rotatably mounted inside the housing, and the guide vane, rotary disc, piston cylinder, and distributor plate are sequentially fitted on the outer side of the central drive shaft. The guide vane, rotary disc, piston cylinder, and distributor plate are all disposed within the housing, and the guide vane and distributor plate are detachably and fixedly connected to the housing. The guide vane is clearance-fitted with the central drive shaft, and the inclined surface of the guide vane is in contact with the rotary disc. The piston cylinder body is fixedly connected to the central drive shaft. Multiple piston grooves are provided on one end face of the piston cylinder body adjacent to the rotary table. Each piston groove is reciprocally slidably connected to one end of a corresponding piston rod. The other end of each piston rod is hinged to a corresponding sliding ball. Each sliding ball is fixedly connected to the rotary table. The axis of each piston rod is parallel to the axis of the central drive shaft. The other end of the piston cylinder body is fitted with an oil distribution plate. Each piston groove has an oil passage corresponding to and communicating with the oil distribution plate. The end of the housing is sealed and fixedly connected to an end cover. The end cover has an oil inlet and an oil outlet corresponding to and communicating with the oil distribution plate.

[0008] Furthermore, the outer wall of each plunger rod and the inner wall of each plunger groove are designed with a fifth-order polynomial streamline shape: y = a5x 5 +a4x 4 +a3x³+a2x²+a1x+a0; where x represents the axial coordinate variable, y represents the radial coordinate variable, and a0, a1, a2, a3, a4, and a5 are polynomial coefficients determined according to actual working conditions and design requirements.

[0009] Furthermore, the contact area between the plunger rod and the plunger groove adopts a gradually transitioning geometry. This gradually transitioning geometry increases the surface area of ​​the transition area, making the stress distribution more uniform, and its geometric parameters have been optimized through finite element analysis.

[0010] Furthermore, each of the plunger rods is made of high-strength alloy steel with a hardened surface.

[0011] Furthermore, each of the plunger rods is provided with an oil permeation channel inside.

[0012] Furthermore, each of the plunger rods has a small oil groove on its outer wall.

[0013] Furthermore, the edges of the oil suction window and the oil pressure window of the oil distribution plate are both transitioned with smooth curves.

[0014] Furthermore, the end cap is provided with an oil inlet chamber and an oil outlet chamber inside. The oil inlet chamber is connected to the oil inlet and the oil suction window of the oil distribution plate. The oil outlet chamber is connected to the oil outlet and the oil pressure window of the oil distribution plate.

[0015] Furthermore, an elastic bellows is also fitted on the outer side of the central drive shaft. One end of the elastic bellows abuts against the inner wall of the plunger cylinder, and the other end abuts against the oil distribution plate.

[0016] The present invention discloses a method for operating an axial piston pump with a streamlined piston system, the method comprising the following steps:

[0017] S1: Power input and synchronous rotary drive:

[0018] The central drive shaft rotates under the drive of an external power source, causing the piston cylinder to rotate synchronously.

[0019] S2: Reciprocating motion conversion:

[0020] The rotation of the piston cylinder body drives multiple piston rods to rotate together. Since the piston rods are fixedly connected to the rotary table through the sliding shoe, the multiple piston rods drive the rotary table to rotate together. When the rotary table rotates, it slides along the inclined surface of the guide swing plate, thereby driving the multiple piston rods to reciprocate relative to the piston cylinder body.

[0021] S3: Oil suction process: When the plunger rod rotates with the plunger cylinder to the oil suction area, the plunger rod moves outward from the plunger cylinder, creating a partial vacuum in the corresponding plunger groove and generating a pressure difference; under the action of this pressure difference, the hydraulic oil enters the oil inlet chamber from the oil inlet of the end cover, and then flows into the corresponding plunger groove through the oil suction window of the distribution plate, completing the oil suction process.

[0022] S4: Oil removal process:

[0023] As the piston cylinder continues to rotate, the piston rod enters the discharge zone along with the piston cylinder. At this time, due to the angle between the rotary table and the guide swing plate, the piston rod is pushed to contract into the piston cylinder, and the hydraulic oil in the piston groove is squeezed, causing the pressure to rise rapidly. The high-pressure hydraulic oil is discharged through the pressure window of the distribution plate to the outlet chamber, and finally enters the external hydraulic system pipeline from the outlet of the end cover, realizing the pressurization and delivery of hydraulic oil.

[0024] Compared with the prior art, the beneficial effects of the present invention are:

[0025] This invention employs a fifth-order polynomial streamlined design for the piston rod and piston groove. By precisely controlling the coefficients of this streamlined curve, the piston system exhibits superior hydrodynamic performance during operation. On one hand, it significantly reduces the frictional resistance between the piston rod and piston groove during reciprocating motion, optimizes force distribution to avoid localized stress concentration, reduces energy loss, and thus extends component lifespan and improves pump operating efficiency. On the other hand, combined with improved shapes of the oil suction and pressure windows on the distribution plate, it optimizes the fluid flow state during oil suction, effectively suppresses cavitation, reduces pump noise and vibration levels, and improves the performance stability of the hydraulic system. This achieves efficient hydraulic oil intake, pressurization, and discharge, meeting the power requirements of hydraulic systems. It is applicable to axial piston pumps of different displacements and pressure ratings, and can be widely used in various industrial hydraulic systems, engineering machinery, aerospace, and other fields, providing hydraulic systems with efficient, stable, and long-life power components. It possesses broad adaptability, promising application prospects, and significant economic benefits. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the structure of the present invention;

[0027] Figure 2 This is a schematic diagram of the plunger rod.

[0028] Figure 3 This is a schematic diagram of the plunger cylinder body;

[0029] Figure 4 This is a schematic diagram of the oil distribution plate;

[0030] Figure 5 This is a schematic diagram of the piston system's assembly.

[0031] Figure 6 This is an exploded view of the plunger system;

[0032] Figure 7 This is a schematic diagram of the end cap structure;

[0033] Figure 8 yes Figure 7 The main view. Detailed Implementation

[0034] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the invention, not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0035] An axial piston pump with a streamlined piston system includes a housing 1, a guide vane 2, a central drive shaft 3, a distribution plate 4, a piston cylinder 5, a rotary disk 6, a sliding shoe 7, a piston rod 9, and an end cap 12. The output end of the central drive shaft 3 is rotatably mounted in the housing 1 via a rear bearing 11 and a front bearing 13. The guide vane 2, the rotary disk 6, the piston cylinder 5, and the distribution plate 4 are sequentially mounted on the outer side of the central drive shaft 3. The guide vane 2, the rotary disk 6, the piston cylinder 5, and the distribution plate 4 are all disposed within the housing 1. The housing 1 provides support and protection to ensure the stable operation of the internal components. The guide vane 2 and the oil distribution plate 4 are detachably fixed to the housing 1 via fixing pins. The guide vane 2 is clearance-fitted with the central drive shaft 3, and the inclined surface of the guide vane 2 is rotatably fitted to the rotary disk 6. The plunger cylinder 5 is fixedly connected to the central drive shaft 3 via a key. Multiple plunger grooves 10 are evenly distributed circumferentially on one end face of the plunger cylinder 5 adjacent to the rotary disk 6. Each plunger groove 10 is reciprocally slidingly connected to one end of a corresponding plunger rod 9, forming a working chamber for hydraulic oil. The other end of each plunger rod 9 is ball-jointed to a corresponding sliding shoe 7, and each sliding shoe 7 is fixedly connected to the rotary disk 6. The sliding shoe 7 transmits power and motion, reduces friction, and improves transmission efficiency. The rotary disk 6 supports and guides the multiple sliding shoes 7, ensuring the stability and accuracy of the plunger rod 9 in reciprocating motion. The rotary disk 6 effectively disperses the pressure from the sliding shoes 7, reducing wear and extending service life. The axis of each plunger rod 9 is parallel to the axis of the central drive shaft 3; the other end of the plunger cylinder 5 is fitted with the oil distribution plate 4, and each plunger groove 10 has an oil passage corresponding to and communicating with the oil distribution plate 4. The end of the housing 1 is fixedly connected to the end cover 12 by bolts to form a sealed space, preventing hydraulic oil leakage and providing additional support and protection. The end cover ensures the sealing and stability of the internal components of the housing, prevents external impurities from entering, and ensures the cleanliness and reliability of the system. The end cover 12 is provided with an oil inlet 121 and an oil outlet 122 corresponding to and communicating with the oil distribution plate 4.

[0036] Furthermore, the outer wall of each plunger rod 9 and the inner wall of each plunger groove 10 are designed with a fifth-order polynomial streamline shape: y = a5x 5 +a4x 4 The equation is: +a3x³ + a2x² + a1x + a0; where x represents the axial coordinate variable, y represents the radial coordinate variable, and a0, a1, a2, a3, a4, and a5 are polynomial coefficients determined according to actual working conditions and design requirements. By precisely controlling these coefficients, the plunger system achieves superior hydrodynamic performance during operation, meeting the needs of axial plunger pumps with different displacements and pressure ratings. Within the appropriate adjustment range, the coefficients ensure that the axial plunger pump maintains optimal performance under various working conditions.

[0037] The fifth-order polynomial streamlined curve gradually contracts at the head of the piston rod 9 and smoothly transitions at the tail, creating a fitting clearance between the piston rod 9 and the piston groove 10. This reduces the contact area between the two, thereby lowering frictional resistance during reciprocating motion, optimizing force distribution, and improving sealing performance, significantly enhancing the energy efficiency of the axial piston pump. Simultaneously, the design fully considers fluid dynamics factors, allowing for smoother hydraulic oil flow around the piston system, reducing eddies and pressure fluctuations, ensuring high efficiency and stability of oil flow, and thus improving the operational stability and safety of the piston pump under high-pressure and high-speed conditions, extending the service life of the piston pump.

[0038] Furthermore, the contact area between the plunger rod 9 and the plunger groove 10 adopts a gradually transitioning geometric structure. This gradually transitioning geometric structure increases the surface area of ​​the transition area, making the stress distribution more uniform, and its geometric parameters have been optimized through finite element analysis. The gradually transitioning geometric structure can reduce stress concentration, reduce energy loss, and optimize the force distribution, making the wear of the plunger system more uniform during long-term operation. This improves the fatigue resistance of the plunger rod 9 and the service life of the plunger system, ensuring the reliability of the plunger pump under high stress conditions.

[0039] The design of the piston system achieves dynamic balance optimization of the plunger rod and plunger groove. This dynamic balance optimization, verified through modal analysis and experiments, reduces vibration and noise during the operation of the plunger pump, making the plunger pump run more smoothly and lowering the noise level.

[0040] Furthermore, each of the plunger rods 9 is made of high-strength alloy steel with a surface hardening treatment. High-strength alloy steel has high strength, and the surface hardening treatment increases the hardness, enhances the durability of the component, improves wear resistance and fatigue resistance, extends the service life of the component, and reduces maintenance costs.

[0041] Furthermore, each of the plunger rods 9 is provided with an axially penetrating oil passage 91 inside, which is used to continuously supply lubricating oil to the contact area between the plunger rod 9 and the plunger groove 10 to form a stable oil film.

[0042] Furthermore, each of the plunger rods 9 has a small oil groove 92 on its outer wall. The shape and size of the small oil groove 92 are optimized to store lubricating oil and ensure that the lubricating oil is evenly distributed on the entire contact surface between the plunger rod 9 and the plunger groove 10, so as to further reduce friction loss and improve sealing performance.

[0043] The fitting clearance between the plunger rod 9 and the plunger groove 10 has been optimized to ensure good lubrication conditions, reduce the risk of oil leakage, thereby extending the service life of components and improving the reliability and operational safety of the hydraulic system.

[0044] Furthermore, the edges of the oil suction window 41 and the oil pressure window 42 of the oil distribution plate 4 both adopt smooth curved transitions. The smooth curved transition of the oil suction window 41 can reduce the resistance and eddies when the hydraulic oil enters, and the smooth curved transition of the oil pressure window 42 can make the discharged high-pressure oil flow out smoothly, reducing pressure fluctuations and turbulence during the oil discharge process; it can improve the uniformity and flow efficiency of the oil flow, reduce energy loss and energy consumption, and at the same time reduce the noise and vibration during the operation of the piston pump, enhancing the stability of the hydraulic system and the operating efficiency of the piston pump.

[0045] Furthermore, the end cap 12 is provided with an oil inlet chamber 123 and an oil outlet chamber 124 inside. The oil inlet chamber 123 is connected to the oil inlet 121 and the oil suction window 41 of the oil distribution plate 4. The oil outlet chamber 124 is connected to the oil outlet 122 and the oil pressure window 42 of the oil distribution plate 4.

[0046] Furthermore, an elastic bellows 8 is also fitted on the outer side of the central drive shaft 3. One end of the elastic bellows 8 abuts against the inner wall of the plunger cylinder 5, and the other end of the elastic bellows 8 abuts against the oil distribution plate 4. The elastic bellows 8 is used to adjust the pressure between the oil distribution plate 4 and the plunger cylinder 5 to ensure that the plunger cylinder 5 and the oil distribution plate 4 are in close contact, and to ensure stable contact with the oil distribution plate 4 during rotation, so as to achieve efficient transmission of hydraulic oil.

[0047] The present invention discloses a method for operating an axial piston pump with a streamlined piston system, the method comprising the following steps:

[0048] S1: Power input and synchronous rotary drive:

[0049] The central drive shaft 3 rotates under the drive of external power. During its rotation, it is supported by the rear bearing 11 and the front bearing 13 in the housing 1 to ensure stable rotation. At the same time, it drives the plunger cylinder 5 to rotate synchronously through the key connection.

[0050] S2: Reciprocating motion conversion:

[0051] The rotary table 6 is in contact with the inclined surface of the guide swing plate 2 and is installed at a certain angle. This angle is the key condition for the reciprocating motion of the plunger rod 9.

[0052] The rotation of the piston cylinder 5 drives multiple piston rods 9 to rotate together. Since the piston rods 9 are fixedly connected to the rotary table 6 through the sliding shoe 7, the multiple piston rods 9 drive the rotary table 6 to rotate together. When the rotary table 6 rotates, it slides along the inclined surface of the guide swing plate 2, thereby driving the multiple piston rods 9 to reciprocate relative to the piston cylinder 5.

[0053] S3: Oil suction process: When the plunger rod 9 rotates with the plunger cylinder 5 to the oil suction area, the plunger rod 9 moves outward from the plunger cylinder 5, creating a partial vacuum in the corresponding plunger groove 10 and generating a pressure difference; under the action of this pressure difference, the hydraulic oil enters the oil inlet chamber 123 from the oil inlet 121 of the end cover 12, and then flows into the corresponding plunger groove 10 through the oil suction window 41 of the oil distribution plate 4, completing the oil suction process;

[0054] S4: Oil removal process:

[0055] As the piston cylinder 5 continues to rotate, the piston rod 9 enters the oil discharge zone along with the piston cylinder 5. At this time, due to the angle between the rotary table 6 and the guide swing plate 2, the piston rod 9 is pushed to retract into the piston cylinder 5, and the hydraulic oil in the piston groove 10 is squeezed, and the pressure rises rapidly. The high-pressure hydraulic oil is discharged through the pressure window 42 of the distribution plate 4 to the oil outlet chamber 124, and finally enters the external hydraulic system pipeline from the oil outlet 122 of the end cover 12, realizing the pressurization and transportation of hydraulic oil.

[0056] Throughout the entire working process, as the plunger cylinder 5 rotates, the plunger hole on it connects sequentially with the plunger groove 10 to the oil suction window 41 and the oil pressure window 42, ensuring that the oil suction and discharge processes are carried out continuously. Furthermore, the precise design of the plunger system, such as its streamlined shape and gradual transition structure, ensures smooth and efficient oil flow, reducing energy loss during the flow process.

[0057] The present invention has the following advantages:

[0058] Significant performance improvement: The five-stage polynomial streamlined piston system greatly reduces friction loss, resulting in a significant improvement in the efficiency of the axial piston pump under high-pressure and high-speed conditions. Compared to traditional designs, the pump's energy consumption is reduced, providing a more powerful output to the hydraulic system while reducing energy waste, resulting in significant energy savings.

[0059] Optimized stress distribution: Through precise profile design, the piston system experiences more uniform stress, avoiding localized stress concentration. This results in more even wear on the piston rod and piston groove during long-term operation, extending component lifespan. Experiments show that under the same operating conditions, the optimized piston system has a longer service life, reducing equipment maintenance costs and downtime.

[0060] Cavitation and Noise Suppression: The optimized piston shape and suction / pressure oil window design improve fluid flow during the oil suction process, effectively suppressing cavitation. Reduced cavitation lowers pump noise and vibration levels, improving system stability. In practical applications, pump noise is reduced, providing a quieter working environment.

[0061] High adaptability: This optimized design is suitable for axial piston pumps of different displacements and pressure ratings, exhibiting wide adaptability. Whether for small hydraulic equipment or large industrial hydraulic systems, the piston system optimization scheme of this invention can achieve improved performance and enhanced reliability.

[0062] Easy to manufacture and maintain: Although the fifth-order polynomial streamlined curve is mathematically complex, with the support of modern CNC machining technology, the required plunger rod and plunger groove shapes can be precisely machined. At the same time, the optimized plunger system has a simple structure, facilitating disassembly and maintenance, and providing convenience for routine equipment upkeep and troubleshooting.

[0063] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of the equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0064] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. An axial piston pump having a streamlined piston system, characterized by: The system includes a housing (1), a guide vane (2), a central drive shaft (3), a distributor plate (4), a piston cylinder (5), a rotary table (6), a sliding shoe (7), a piston rod (9), and an end cap (12). The output end of the central drive shaft (3) is rotatably mounted inside the housing (1). The guide vane (2), rotary table (6), piston cylinder (5), and distributor plate (4) are sequentially mounted on the outer side of the central drive shaft (3). The guide vane (2), rotary table (6), piston cylinder (5), and distributor plate (4) are all located inside the housing (1). The guide vane (2) and distributor plate (4) are detachably and fixedly connected to the housing (1). The guide vane (2) is clearance-fitted with the central drive shaft (3). The inclined surface of the guide vane (2) is rotatably and closely connected to the rotary table (6). The piston cylinder (5)... The piston cylinder body (5) is fixedly connected to the central drive shaft (3). A plurality of piston grooves (10) are provided on one end face of the piston cylinder body (5) adjacent to the rotary table (6). Each piston groove (10) is reciprocally slidably connected to one end of the corresponding piston rod (9). The other end of each piston rod (9) is ball-jointed with the corresponding sliding shoe (7). Each sliding shoe (7) is fixedly connected to the rotary table (6). The axis of each piston rod (9) is parallel to the axis of the central drive shaft (3). The other end of the piston cylinder body (5) is fitted with the oil distribution plate (4). Each piston groove (10) is provided with an oil passage corresponding to the oil distribution plate (4). The end of the housing (1) is sealed and fixedly connected to the end cover (12). The end cover (12) is provided with an oil inlet (121) and an oil outlet (122) corresponding to the oil distribution plate (4).

2. An axial piston pump having a streamlined piston system according to claim 1, characterized in that: The outer wall of each said plunger rod (9) and the inner wall of each plunger groove (10) are designed with a quintic polynomial streamline: y = a5x 5 + a4x 4 + a3x³ + a2x² + a1x + a0; wherein x represents an axial coordinate variable, y represents a radial coordinate variable, a0, a1, a2, a3, a4 and a5 are polynomial coefficients determined according to actual working conditions and design requirements.

3. An axial piston pump with a streamlined piston system according to claim 2, characterized in that: The contact area between the plunger rod (9) and the plunger groove (10) adopts a gradually transitioning geometric structure. The gradually transitioning geometric structure increases the surface area of ​​the transition area to make the stress distribution more uniform, and its geometric parameters are optimized by finite element analysis.

4. An axial piston pump with a streamlined piston system according to claim 3, characterized in that: Each of the plunger rods (9) is made of high-strength alloy steel with a hardened surface.

5. An axial piston pump with a streamlined piston system according to claim 4, characterized in that: Each of the plunger rods (9) has an internal oil permeation channel (91).

6. An axial piston pump with a streamlined piston system according to claim 1, characterized in that: Each of the plunger rods (9) has a small oil groove (92) on its outer wall.

7. An axial piston pump with a streamlined piston system according to claim 5 or 6, characterized in that: The edges of the oil suction window (41) and the oil pressure window (42) of the oil distribution plate (4) are both transitioned with smooth curves.

8. An axial piston pump with a streamlined piston system according to claim 7, characterized in that: The end cap (12) is provided with an oil inlet chamber (123) and an oil outlet chamber (124). The oil inlet chamber (123) is connected to the oil inlet (121) and the oil suction window (41) of the oil distribution plate (4). The oil outlet chamber (124) is connected to the oil outlet (122) and the oil pressure window (42) of the oil distribution plate (4).

9. An axial piston pump with a streamlined piston system according to claim 1, characterized in that: An elastic bellows (8) is also fitted on the outside of the central drive shaft (3). One end of the elastic bellows (8) abuts against the inner wall of the plunger cylinder (5), and the other end of the elastic bellows (8) abuts against the oil distribution plate (4).

10. A method of operating an axial piston pump with a streamlined piston system according to any one of claims 1-9, characterized in that: The method includes the following steps: S1: Power input and synchronous rotary drive: The central drive shaft (3) rotates under the drive of external power, causing the plunger cylinder (5) to rotate synchronously; S2: Reciprocating motion conversion: The rotation of the piston cylinder (5) drives multiple piston rods (9) to rotate together. Since the piston rods (9) are fixedly connected to the rotary table (6) through the sliding shoe (7), the multiple piston rods (9) drive the rotary table (6) to rotate together. When the rotary table (6) rotates, it slides along the inclined plane of the guide swing plate (2), thereby driving the multiple piston rods (9) to reciprocate relative to the piston cylinder (5). S3: Oil suction process: When the plunger rod (9) rotates with the plunger cylinder (5) to the oil suction area, the plunger rod (9) moves outward from the plunger cylinder (5), so that a partial vacuum is formed in the corresponding plunger groove (10), generating a pressure difference; under the action of this pressure difference, the hydraulic oil enters the oil inlet chamber (123) from the oil inlet (121) of the end cover (12), and then flows into the corresponding plunger groove (10) through the oil suction window (41) of the oil distribution plate (4), thus completing the oil suction; S4: Oil removal process: As the piston cylinder (5) continues to rotate, the piston rod (9) enters the oil discharge area along with the piston cylinder (5); at this time, the rotary table (6) pushes the piston rod (9) to contract into the piston cylinder (5) due to the angle between the rotary table (6) and the guide swing plate (2), and the hydraulic oil in the piston groove (10) is squeezed and the pressure rises rapidly; the high-pressure hydraulic oil is discharged to the oil outlet chamber (124) through the oil pressure window (42) of the distribution plate (4), and finally enters the external hydraulic system pipeline from the oil outlet (122) of the end cover (12), realizing the pressurization and transportation of hydraulic oil.

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