A high-pressure valve porting plunger pump

Abstract

The application discloses a high-pressure valve flow distribution plunger pump and belongs to the technical field of hydraulic system power sources. The high-pressure valve flow distribution plunger pump comprises a shell, a first through hole is formed in the side wall of the shell, the first through hole is communicated with an oil passage in the shell, one end of the shell is provided with an end cover, the other end of the shell is provided with an oil outlet interface, a main shaft swash plate is arranged in the shell, one end of the main shaft swash plate extends out of the end cover, the other end of the main shaft swash plate is provided with a plurality of plungers, a plunger cylinder is fixedly arranged on one side of the shell close to the oil outlet interface, the plunger cylinder is provided with a plunger hole matched with the plunger, a return spring is arranged on the plunger, the plunger is of a hollow structure, an oil suction check valve is arranged in the side of the plunger close to the plunger cylinder, and an oil discharge check valve is arranged in the plunger hole in the plunger cylinder. The high-pressure valve flow distribution plunger pump has the advantages of light weight, small size, high pressure and high power density, and can meet the use requirements of most hydraulic systems.

Description

Technical Field

[0001] This invention relates to the technical field of hydraulic system power sources, and more specifically, to a high-pressure valve distribution piston pump. Background Technology

[0002] To ensure the normal operation of a hydraulic system, a power source is essential. As the core component of a hydraulic system, the hydraulic pump must have higher reliability and performance than conventional hydraulic pumps in some important fields. Currently, the most widely used positive displacement pumps are gear pumps and piston pumps.

[0003] A gear pump is a commonly used rotary positive displacement pump, mainly composed of two meshing gears, one driving gear and the other driven gear, as well as a pump casing and a pump cover. When the two gears rotate relative to each other, the sealed volume formed between the gear teeth and between the gear casing changes with the rotation of the gears, thereby achieving the purpose of pumping and discharging liquid. The advantages of gear pumps are their relatively simple structure and strong self-priming ability, but their disadvantages are also obvious. Gear pumps suffer from radial force imbalance, significant leakage at the tooth tips and between the teeth, difficulty in achieving high pressure, and generally low volumetric efficiency, among other problems.

[0004] A plunger pump is a commonly used reciprocating positive displacement pump, mainly composed of a pump body, plunger, slide block, and various valves. The plunger reciprocates within the pump body, and in conjunction with the action of a check valve, it achieves the intake and discharge of liquid. Plunger pumps have a compact structure, low media leakage, higher volumetric efficiency, and can achieve high speed and high pressure. Therefore, compared to the many shortcomings of gear pumps, plunger pumps have higher reliability under high-pressure conditions.

[0005] However, traditional piston pumps are large in size, and there is an urgent need to design a lightweight, high-pressure, and high-power-density high-pressure valve distribution piston pump to broaden the application scope of hydraulic transmission technology. Summary of the Invention

[0006] This invention provides a high-pressure valve-distributed plunger pump to achieve lightweight, high-pressure, and high-power-density plunger pumps.

[0007] To solve the above-mentioned technical problems, the technical solution of the present invention is as follows:

[0008] A high-pressure valve distribution plunger pump includes a housing, wherein a first through hole is provided on the side wall of the housing, and the first through hole is connected to an oil passage inside the housing;

[0009] An end cap is installed at one end of the housing, and an oil outlet is installed at the other end of the housing; a spindle swashplate is installed inside the housing, one end of the spindle swashplate extends out of the end cap, and a plurality of plungers are provided at the other end of the spindle swashplate;

[0010] A plunger cylinder is fixedly installed inside the housing on the side near the oil outlet. The plunger cylinder has a plunger hole adapted to the plunger. A return spring is fitted on the plunger to enable the plunger to reciprocate in the plunger hole as the spindle swashplate rotates.

[0011] Compared to ordinary plunger pumps, the plunger cylinder of this small pump is fixed and does not rotate with the main shaft;

[0012] The plunger has a hollow structure. An oil suction port is provided on the side wall of the plunger away from the plunger cylinder. An oil suction check valve is installed inside the side of the plunger close to the plunger cylinder. An oil discharge check valve is installed in the plunger hole inside the plunger cylinder.

[0013] In this disclosure, an oil suction check valve is disposed inside the plunger, and an oil suction port is opened at the upper end of the plunger; a pressure check valve is disposed inside the plunger cylinder; it has the advantages of being lightweight, small in size, high-pressure and high-power density, and can meet the needs of most hydraulic systems.

[0014] This high-pressure valve-distribution piston pump features an excellent design that enables it to perform exceptionally well in handling challenges such as high pressure and high power output. Specifically, one end of the housing is secured to the end cover, while the other end is equipped with an oil outlet, forming a complete pressure closed loop. This loop ensures that the pump fluid always flows within the loop, significantly improving the efficiency of hydraulic conversion. Furthermore, one end of the spindle swashplate extends from the end cover, while the other end connects to multiple pistons, facilitating the conversion from rotary motion to reciprocating linear motion and meeting the requirements of hydraulic equipment.

[0015] Furthermore, unlike traditional piston pumps, the piston cylinder in this pump is fixed and does not rotate with the swashplate. This design saves energy, reduces wear, and extends the equipment's lifespan. The piston cylinder has internal bores adapted to the piston, facilitating efficient reciprocating motion driven by the swashplate. Overall, the main advantages of this design are lightweight design, compact size, high pressure capability, and high power density, enabling this high-pressure valve-distribution piston pump to meet the needs of most hydraulic systems.

[0016] Furthermore, a lip seal is installed on the end cap to prevent hydraulic oil leakage.

[0017] Furthermore, a deep groove ball bearing for supporting the rotational movement of the spindle swashplate and a thrust bearing for supporting the axial load of the spindle swashplate are installed between the housing and the spindle swashplate.

[0018] In this disclosure, a lip seal is installed on the end cap, adding an extra layer of leak-proof protection to the hydraulic system. The lip seal is an excellent static sealing element; its special shape creates a good seal at the interface, preventing hydraulic oil leakage. This design not only protects the internal components of the equipment and reduces oil loss, but also facilitates normal equipment operation, improves operating efficiency, and reduces operating costs.

[0019] Deep groove ball bearings and thrust bearings are installed between the housing and the swashplate. Deep groove ball bearings are a type of bearing that provides high-precision raceways and high load-carrying capacity at high speeds. They bear the radial load of the swashplate during rotation, maintaining its smooth operation. Thrust bearings, on the other hand, support the axial load of the swashplate, preventing displacement during operation and ensuring high efficiency and low-error working accuracy. These design features enhance the stability of the equipment and improve its reliability during long-term operation.

[0020] Furthermore, one end of the plunger is connected to the main shaft swashplate via a plunger ball head to realize the reciprocating motion of the plunger; the plunger ball head at the plunger end directly contacts the main shaft swashplate to reduce leakage of the slipper pair and improve the efficiency of the pump.

[0021] The plunger head has no slipper, and there is a return spring between the plunger and the plunger cylinder. The return spring is compressed during the plunger's oil pressing movement. When the plunger reaches the right dead center position, the return spring is compressed to its maximum.

[0022] During the oil suction process of the plunger, the return spring does positive work, assisting the plunger's oil suction movement and overcoming hydraulic pressure to increase the oil suction volume.

[0023] In this disclosure, one end of the plunger contacts the swashplate via a plunger ball head, enabling the plunger to perform efficient reciprocating motion. This design further improves the conversion efficiency from rotary motion to linear reciprocating motion, increasing the performance of the high-pressure valve distribution plunger pump. The plunger ball head contact with the swashplate reduces leakage from the slipper assembly, improving pump utilization efficiency and extending equipment lifespan.

[0024] The plunger is connected to the spindle swashplate by a plunger ball head, reducing additional friction and leakage caused by slippers, thereby maximizing the overall efficiency of the pump. A return spring is installed between the plunger and the plunger cylinder. During the plunger's oil-pressing motion, the return spring is compressed; during the plunger's oil-suction motion, the release of the spring's stored potential energy provides the necessary thrust to the plunger, overcoming the resistance from the hydraulic pressure and enabling the plunger to successfully complete the oil-suction motion. This design improves the performance of the high-pressure valve-distributed plunger pump, helping to meet more diverse application requirements.

[0025] Furthermore, the oil suction check valve includes an oil suction valve seat, an oil suction valve spring, and an oil suction valve core. The oil suction valve seat is fixedly installed inside the plunger to provide a fixed support structure for the oil suction valve spring and the oil suction valve core. The oil suction valve spring is sleeved on the oil suction valve core.

[0026] Furthermore, the drain valve includes a drain valve seat, a drain valve spring, and a drain valve core. The drain valve seat is fixedly installed in the plunger hole to provide a fixed support structure for the drain valve spring and the drain valve core. The drain valve spring is sleeved on the drain valve core.

[0027] In this disclosure, during one revolution of the spindle swashplate, when the plunger moves to the left and increases the volume of the plunger cavity, the pressure inside the cavity gradually decreases until a negative pressure appears. At this time, under the action of the pressure before and after the suction check valve, the suction valve core is forced to overcome the suction valve spring and is opened, so that the plunger cavity continuously sucks in oil.

[0028] When the plunger moves to the right, causing the volume in the plunger chamber to gradually decrease, the oil in the chamber is continuously compressed due to the decrease in volume, which in turn increases the oil pressure in the chamber. As the force on the valve core of the right-side drain valve increases, the valve is opened, causing the oil in the chamber to flow out from the drain valve, thus completing the draining process.

[0029] The motor rotates, driving the swashplate of the main shaft to move. The plunger then repeatedly moves in a straight line within the fixed cylinder, continuously repeating the above suction and discharge process, thus enabling the small pump to continuously suction and discharge oil.

[0030] In this disclosure, the design of the suction check valve and the discharge check valve is crucial. The suction check valve includes a suction valve seat, a suction valve spring, and a suction valve spool. The suction valve seat provides a stable support structure for the suction valve spring and the suction valve spool. When negative pressure is generated in the plunger chamber, the suction valve spool overcomes the suction valve spring and opens, achieving efficient oil suction. Similarly, the discharge check valve includes a discharge valve seat, a discharge valve spring, and a discharge valve spool. The discharge valve seat provides a stable support structure for the discharge valve spring and the discharge valve spool. When the volume decreases and the oil pressure increases, the force on the discharge valve spool increases, the valve opens, and oil continuously flows out of the chamber. The characteristics of these two check valves enable the plunger pump to effectively perform the suction and discharge processes, thereby achieving a highly efficient hydraulic system.

[0031] Furthermore, this high-pressure valve-distribution piston pump can adapt to continuous operation requirements. Driven by a motor-driven swashplate, the piston continuously reciprocates linearly within a fixed cylinder, repeatedly performing the suction and discharge processes. This design results in higher pump efficiency, meeting the practical application needs of many hydraulic systems. In addition, this piston pump is compact, durable, and has high power density, combining high performance with portability, making it widely applicable in various hydraulic equipment.

[0032] Furthermore, the spindle swashplate includes a spindle and a swashplate connected to each other, and the swashplate has an inclination angle in the radial direction; structurally, the spindle and the swashplate are integrated into one unit, and the inclined surface of the spindle swashplate has a certain inclination angle in the radial direction. Under the drive of the motor, the spindle swashplate rotates, causing the plunger to reciprocate in the plunger hole of the plunger cylinder.

[0033] Furthermore, one end of the spindle extends out of the end cover, and the portion of the spindle extending out of the end cover is connected to a drive mechanism for driving the spindle swashplate to rotate.

[0034] Furthermore, the high-pressure valve distribution plunger pump is fixedly installed inside a sealed oil tank by bolts. The oil tank contains oil, and the oil in the oil tank enters the oil passage inside the high-pressure valve distribution plunger pump through the first through hole.

[0035] This disclosure uses a bolted structure to fix the high-pressure valve distribution plunger pump in a sealed oil tank, so that the high-pressure valve distribution plunger pump is completely immersed in the oil in the tank. The oil in the tank fills the pump body through the first through hole in the housing, so there is an oil film lubrication inside the entire pump. When the pump is stationary, the pressure inside the pump is equal to the pressure of the oil in the tank, that is, the reference zero pressure of the pump is equal to the pressure of the oil in the sealed oil tank.

[0036] In this disclosure, the spindle swashplate design incorporates the interconnection of the spindle and the swashplate, with the swashplate having a radial inclination angle. This structure effectively integrates the spindle and the swashplate into a single unit, thereby enhancing the overall durability and stability of the equipment. When the motor drives the spindle swashplate to rotate, due to the inclination angle of the inclined plane, the plunger can make precise reciprocating motion in the plunger bore of the plunger cylinder, achieving an effective conversion between rotary motion and reciprocating motion.

[0037] To further improve operational efficiency, the spindle extends from the end cover and is connected to a drive mechanism that rotates the spindle swashplate. This configuration allows the driving force to be transmitted more directly and efficiently to the spindle swashplate, thus achieving efficient reciprocating motion of the plunger. Furthermore, the entire high-pressure valve distribution plunger pump is bolted into a sealed oil tank, utilizing the oil in the tank for further lubrication and cooling of all components. The oil in the tank fills the pump's periphery through the first through-hole in the housing, forming a continuous and uniform oil film, effectively reducing friction, extending equipment life, and enhancing stability and reliability. When the pump is not running, the pressure inside remains consistent with the pressure of the oil in the tank, achieving excellent pressure stability and further improving work efficiency.

[0038] Compared with the prior art, the beneficial effects of the technical solution of the present invention are:

[0039] 1. Lightweight, compact, high-pressure, and high-power-density: This plunger pump features a compact design and can withstand higher pressures and generate greater power output, while its small size makes it suitable for various space-constrained applications;

[0040] 2. Spindle swashplate motion conversion: Through the design of the spindle swashplate, the rotary motion is converted into the reciprocating linear motion of the piston, realizing efficient hydraulic conversion and meeting the needs of hydraulic equipment;

[0041] 3. Fixed plunger cylinder: Unlike traditional plunger pumps, this design has a fixed plunger cylinder that does not rotate with the rotation of the spindle swashplate, saving energy consumption, reducing equipment wear, and extending service life;

[0042] 4. Hollow structure of the plunger and return spring: The plunger adopts a hollow structure, which allows oil to be drawn through the plunger. An oil suction check valve is installed at the oil suction end of the plunger, thereby realizing an efficient oil suction process. At the same time, a return spring is installed between the plunger and the plunger cylinder to provide positive thrust to the plunger, overcome the resistance caused by hydraulic pressure, and ensure normal oil suction movement.

[0043] 5. Suction check valve and discharge check valve: The design of the suction check valve and discharge check valve enables effective hydraulic oil intake and discharge; during the piston movement, when negative pressure is generated in the cavity, the suction check valve opens to achieve oil intake; when the oil in the cavity is compressed, the discharge check valve opens to achieve oil discharge.

[0044] 6. The high-pressure valve distribution plunger pump is fixed in a sealed oil tank: By fixing the pump in a sealed oil tank, the entire pump is completely immersed in the oil, achieving continuous oil lubrication; the oil in the tank enters the oil passage in the pump through the through hole on the housing, maintaining the pump's lubrication. At the same time, when the pump stops running, the pressure inside the pump is equal to the oil pressure in the tank, achieving pressure stability.

[0045] 7. Other structural optimizations: The plunger head is connected to the spindle swashplate via a plunger ball head, reducing leakage from the slipper pair and improving pump efficiency; a lip seal is installed on the end cover to prevent oil leakage; deep groove ball bearings and thrust bearings are installed between the housing and the spindle swashplate, enhancing the stability of the equipment. Attached Figure Description

[0046] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0047] Figure 1This is a schematic diagram of the high-pressure valve distribution plunger pump of the present invention;

[0048] Figure 2 This is a three-dimensional structural schematic diagram of the high-pressure valve distribution plunger pump of the present invention;

[0049] Figure 3 This is a side view of the oil outlet side of the high-pressure valve distribution plunger pump of the present invention;

[0050] Figure 4 This is a schematic diagram illustrating the working principle of the high-pressure valve distribution plunger pump in the oil suction stage of the present invention.

[0051] Figure 5 This is a schematic diagram illustrating the working principle of the high-pressure valve distribution plunger pump in the oil discharge stage of the present invention.

[0052] The markings in the diagram are as follows: 1. End cap; 2. Lip seal; 3. Deep groove ball bearing; 4. Thrust bearing; 5. Piston; 6. Return spring; 7. Piston cylinder; 8. Oil outlet port; 9. Discharge valve seat; 10. Discharge valve spring; 11. Discharge valve core; 12. Suction valve seat; 13. Suction valve spring; 14. Suction valve core; 15. Piston ball head; 16. Spindle swashplate; 17. Housing; 18. First through hole. Detailed Implementation

[0053] To better understand the purpose, structure, and function of this invention, the technical solution of this invention will be further described in detail below with reference to the accompanying drawings and specific preferred embodiments.

[0054] In the description of this invention, it should be understood that the terms "left side," "right side," "upper part," "lower part," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. "First," "second," etc., do not indicate the importance of components, and therefore should not be construed as a limitation of the invention. The specific dimensions used in the embodiments are only for illustrating the technical solutions and do not limit the scope of protection of the invention. It is understandable that some well-known structures and their descriptions may be omitted in the accompanying drawings for those skilled in the art.

[0055] Unless otherwise expressly specified and limited, the terms "installation," "setting," "connection," and "fixation" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0056] Example 1:

[0057] like Figure 1-3 As shown, the present invention provides a technical solution: a high-pressure valve distribution plunger pump, including a housing 17, wherein a first through hole 18 is provided on the side wall of the housing 17, and the first through hole 18 is connected to the oil passage inside the housing 17.

[0058] One end of the housing 17 is fitted with an end cap 1, and the other end of the housing 17 is fitted with an oil outlet port 8; a spindle swashplate 16 is installed inside the housing 17, one end of the spindle swashplate 16 extends out of the end cap 1, and the other end of the spindle swashplate 16 is provided with a plurality of plungers 5.

[0059] A plunger cylinder 7 is fixedly installed inside the housing 17 on the side near the oil outlet port 8. The plunger cylinder 7 has a plunger hole adapted to the plunger 5. A return spring 6 is fitted on the plunger 5 to enable the plunger 5 to reciprocate in the plunger hole as the spindle swashplate 16 rotates.

[0060] Compared to ordinary plunger pumps, the plunger cylinder 7 of this small pump is fixed and does not rotate with the main shaft;

[0061] The plunger 5 has a hollow structure. An oil suction port is provided on the side wall of the plunger 5 away from the plunger cylinder 7. An oil suction check valve is installed inside the side of the plunger 5 close to the plunger cylinder 7. An oil discharge check valve is installed in the plunger hole inside the plunger cylinder 7.

[0062] In this embodiment, the suction check valve is installed inside the plunger 5, and an oil suction port is opened at the upper end of the plunger 5; the pressure check valve is installed inside the plunger cylinder 7; it has the advantages of being lightweight, small in size, high-pressure and high-power density, and can meet the needs of most hydraulic systems.

[0063] This high-pressure valve-distribution piston pump features an excellent design that enables it to perform exceptionally well in handling challenges such as high pressure and high power output. Specifically, one end of the housing 17 is fastened to the end cover 1, while the other end of the housing is equipped with an oil outlet port 8, forming a complete pressure closed loop. This ensures that the oil inside the pump flows within this closed loop at all times, significantly improving the efficiency of hydraulic conversion. Furthermore, one end of the swashplate 16 extends from the end cover 1, while the other end is connected to multiple pistons 5, realizing the conversion from rotary motion to reciprocating linear motion and meeting the requirements of hydraulic equipment.

[0064] Furthermore, unlike traditional piston pumps, the piston cylinder 7 in this pump is fixed and does not rotate with the swashplate 16. This design saves energy, reduces wear, and extends the equipment's service life. The piston cylinder 7 has a piston bore adapted to the piston 5, facilitating efficient reciprocating motion of the piston under the drive of the swashplate. In summary, the main advantages of this design are its lightweight, compact size, high pressure capability, and high power density, enabling this high-pressure valve-distribution piston pump to meet the needs of most hydraulic systems.

[0065] Example 2:

[0066] Based on Embodiment 1, a lip seal 2 is installed on the end cap 1 to prevent hydraulic oil leakage.

[0067] Furthermore, a deep groove ball bearing 3 for supporting the rotational movement of the spindle swashplate 16 and a thrust bearing 4 for supporting the axial load of the spindle swashplate 16 are installed between the housing 17 and the spindle swashplate 16.

[0068] In this embodiment, by installing a lip seal 2 on the end cap 1, an additional layer of leak-proof protection is added to the hydraulic system. The lip seal is an excellent static sealing element; its special shape creates a good seal at the interface, preventing hydraulic oil leakage. This design not only protects the internal components of the equipment and reduces oil loss, but also facilitates normal equipment operation, improves operating efficiency, and reduces operating costs.

[0069] A deep groove ball bearing 3 and a thrust bearing 4 are installed between the housing 17 and the spindle swashplate 16. The deep groove ball bearing is a type of bearing that provides high-precision raceways and high load-carrying capacity at high speeds. It bears the radial load of the spindle swashplate during rotation, maintaining its smooth operation. The thrust bearing, on the other hand, supports the axial load of the spindle swashplate, preventing displacement during operation and ensuring high-efficiency, low-error working accuracy. These design features enhance the stability of the equipment and improve its reliability during long-term operation.

[0070] Example 3:

[0071] Based on Embodiment 1, one end of the plunger 5 is connected to the main shaft swashplate 16 via a plunger ball head 15 to realize the reciprocating motion of the plunger 5; the plunger ball head 15 at the end of the plunger directly contacts the main shaft swashplate 16 to reduce leakage of the slipper pair and improve the efficiency of the pump.

[0072] The head of the plunger 5 has no slipper. There is a return spring 6 between the plunger 5 and the plunger cylinder 7. The return spring 6 is compressed during the oil pressing movement of the plunger. When the plunger 5 moves to the right dead point position, the return spring 6 is compressed to the tightest.

[0073] During the oil suction process of the plunger, the return spring 6 does positive work, assisting the oil suction movement of the plunger 5, overcoming the hydraulic pressure and increasing the oil suction volume.

[0074] In this embodiment, one end of the plunger 5 contacts the main shaft swashplate 16 via the plunger ball head 15, enabling the plunger to complete efficient reciprocating motion. This design further improves the conversion efficiency from rotary motion to linear reciprocating motion, increasing the performance of the high-pressure valve distribution plunger pump. The contact between the plunger ball head 15 and the main shaft swashplate 16 reduces leakage from the slipper pair, improving pump utilization efficiency and extending equipment lifespan.

[0075] The plunger 5 is connected to the main shaft swashplate 16 by the plunger ball head 15, reducing additional friction and leakage caused by the slipper, thereby maximizing the overall efficiency of the pump. A return spring 6 is installed between the plunger 5 and the plunger cylinder 7. During the oil-pressing motion of the plunger 5, the return spring is compressed. During the oil-suction motion of the plunger 5, the release of the potential energy stored in the spring provides the necessary thrust to the plunger 5, overcoming the resistance caused by the hydraulic pressure and enabling the plunger 5 to successfully complete the oil-suction motion. This design improves the performance of the high-pressure valve-distributed plunger pump and helps meet more diverse application requirements.

[0076] Example 4:

[0077] Based on Embodiment 1, the oil suction check valve includes an oil suction valve seat 12, an oil suction valve spring 13, and an oil suction valve core 14. The oil suction valve seat 12 is fixedly installed inside the plunger 5 to provide a fixed support structure for the oil suction valve spring 13 and the oil suction valve core 14. The oil suction valve spring 13 is sleeved on the oil suction valve core 14.

[0078] Furthermore, the drain valve includes a drain valve seat 9, a drain valve spring 10, and a drain valve core 11. The drain valve seat 9 is fixedly installed in the plunger hole to provide a fixed support structure for the drain valve spring 10 and the drain valve core 11. The drain valve spring 10 is sleeved on the drain valve core 11.

[0079] In this embodiment, during one revolution of the spindle swashplate 16, when the plunger 5 moves to the left and increases the volume of the plunger cavity, the pressure in the cavity gradually decreases until a negative pressure appears. At this time, under the action of the pressure before and after the suction check valve, the suction valve core 14 is forced to overcome the suction valve spring 13 and is opened, so that the plunger cavity continuously sucks in oil.

[0080] When the plunger 5 moves to the right, causing the volume in the plunger cavity to gradually decrease, the oil in the cavity is continuously compressed due to the decrease in volume, which in turn increases the oil pressure in the cavity. As the force on the valve core 11 of the right-side drain valve increases, the valve is opened, causing the oil in the cavity to flow out from the drain valve, and finally completing the draining.

[0081] The rotation of the motor drives the main shaft swashplate 16 to move, and the plunger 5 will repeatedly perform reciprocating linear motion in the fixed cylinder, continuously repeating the above suction and discharge process, so that the small pump can continuously suction and discharge oil.

[0082] In this embodiment, the design of the suction check valve and the discharge check valve is crucial. The suction check valve includes a suction valve seat 12, a suction valve spring 13, and a suction valve core 14. The suction valve seat 12 provides a stable support structure for the suction valve spring 13 and the suction valve core 14. When negative pressure is generated in the plunger cavity, the suction valve core 14 is forced to open against the suction valve spring 13, achieving efficient oil suction. Similarly, the discharge check valve includes a discharge valve seat 9, a discharge valve spring 10, and a discharge valve core 11. The discharge valve seat 9 provides a stable support structure for the discharge valve spring 10 and the discharge valve core 11. When the volume decreases and the oil pressure increases, the force on the discharge valve core 11 increases, the valve opens, and the oil in the cavity flows out continuously. The characteristics of these two check valves enable the plunger pump to effectively perform the suction and discharge processes, thereby achieving a highly efficient hydraulic system.

[0083] Furthermore, this high-pressure valve-distributed piston pump can adapt to continuous operation requirements. Driven by a motor, the main shaft swashplate 16 allows the piston 5 to continuously reciprocate linearly within a fixed cylinder, repeatedly performing the suction and discharge processes. This design results in higher pump efficiency, meeting the practical application needs of many hydraulic systems. In addition, this piston pump is compact, durable, and has high power density, combining high performance with portability, making it widely applicable in various hydraulic equipment.

[0084] Example 5:

[0085] Based on Embodiment 1, the spindle swashplate 16 includes a spindle and a swashplate connected to each other, and the swashplate has an inclination angle in the radial direction; structurally, the spindle and the swashplate are integrated into one unit, and the inclined surface of the spindle swashplate 16 has a certain inclination angle in the radial direction. Under the drive of the motor, the spindle swashplate 16 rotates, causing the plunger 5 to reciprocate in the plunger hole of the plunger cylinder 7.

[0086] Furthermore, one end of the spindle extends out of the end cover 1, and the portion of the spindle extending out of the end cover 1 is connected to a drive mechanism for driving the spindle swashplate 16 to rotate.

[0087] Furthermore, the high-pressure valve distribution plunger pump is fixedly installed inside a sealed oil tank by bolts. The oil tank contains oil, and the oil in the oil tank enters the oil passage inside the high-pressure valve distribution plunger pump through the first through hole 18.

[0088] In this embodiment, the high-pressure valve distribution plunger pump is fixed in a sealed oil tank by bolts, so that the high-pressure valve distribution plunger pump is completely immersed in the oil in the tank. The oil in the tank fills the pump through the first through hole 18 in the housing 17, so there is an oil film lubrication inside the entire pump. When the pump is stationary, the pressure inside the pump is equal to the pressure of the oil in the tank, that is, the reference zero pressure of the pump is equal to the pressure of the oil in the sealed oil tank.

[0089] In this embodiment, the spindle swashplate 16 is designed with the spindle and swashplate interconnected. The swashplate has a radial angle, which effectively integrates the spindle and swashplate into one unit, thereby enhancing the overall durability and stability of the equipment. When the motor drives the spindle swashplate 16 to rotate, due to the angle of the inclined surface, the plunger 5 can make precise reciprocating motion in the plunger hole of the plunger cylinder 7, realizing an effective conversion between rotary motion and reciprocating motion.

[0090] To further improve operational efficiency, the spindle extends from the end cover 1 and is connected to a drive mechanism that rotates the spindle swashplate 16. This configuration allows the driving force to be transmitted more directly and efficiently to the spindle swashplate 16, thereby achieving efficient reciprocating motion of the plunger 5. Furthermore, the entire high-pressure valve distribution plunger pump is bolted to a sealed oil tank, utilizing the oil in the tank for further lubrication and cooling of all components. The oil in the tank fills the pump's periphery through the first through-hole 18 in the housing 17, forming a continuous and uniform oil film, effectively reducing friction, extending equipment life, and enhancing equipment stability and reliability. When the pump is not in operation, the pressure inside remains consistent with the pressure of the oil in the tank, achieving excellent pressure stability and contributing to improved work efficiency.

[0091] like Figure 4-5 As shown, Figure 4 This is a schematic diagram illustrating the working principle of the high-pressure valve distribution plunger pump in the oil suction stage of the present invention. Figure 5 This is a schematic diagram of the working principle of the high-pressure valve distribution plunger pump in the oil discharge stage of the present invention; the oil suction and oil discharge processes are two very critical links in the hydraulic system.

[0092] Oil suction process: When the hydraulic pump is working, when the plunger 5 moves backward or when the plunger 5 retracts in the plunger cylinder 7 due to the rotation of the swashplate, a low-pressure area or negative pressure is formed inside the plunger cavity, which causes the internal volume of the pump to increase, creating a space for oil suction. In this case, the oil suction valve core 14 will overcome the resistance of the oil suction valve spring 13 and open the oil suction check valve because the pressure in the external oil circuit is greater than the pressure inside the valve. The oil then enters the plunger cavity through the oil suction pipe and the oil suction valve, completing the oil suction process.

[0093] Oil discharge process: When the plunger 5 moves forward or is in the forward stage due to the drive of the swashplate, the volume of the plunger chamber begins to decrease, compressing the oil in the chamber; at this time, the pressure of the oil in the chamber increases. When this pressure is greater than the resistance of the oil discharge valve spring 10, the oil discharge valve core 11 will be pushed open, opening the oil discharge check valve; at this time, the high-pressure oil is discharged and flows to the working components of the system, completing the oil discharge process.

[0094] The processes of oil suction and oil discharge are continuously repeated during pump operation, thus enabling the continuous operation of the hydraulic system.

[0095] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation of the present invention. Those skilled in the art can make other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the claims of the present invention.

Claims

1. A high-pressure valve distribution plunger pump, characterized in that: Includes a housing (17), the side wall of which is provided with a first through hole (18), the first through hole (18) being connected to an oil passage inside the housing (17); One end of the housing (17) is fitted with an end cap (1), and the other end of the housing (17) is fitted with an oil outlet port (8); a spindle swashplate (16) is installed inside the housing (17), one end of the spindle swashplate (16) extends out of the end cap (1), and the other end of the spindle swashplate (16) is provided with several plungers (5). A plunger cylinder (7) is fixedly installed inside the housing (17) on the side near the oil outlet (8). The plunger cylinder (7) has a plunger hole adapted to the plunger (5). A return spring (6) is sleeved on the plunger (5) to enable the plunger (5) to reciprocate in the plunger hole as the spindle swashplate (16) rotates. The plunger (5) has a hollow structure. An oil suction check valve is installed inside the plunger (5) on the side near the plunger cylinder (7). An oil discharge check valve is installed in the plunger hole inside the plunger cylinder (7). The oil suction check valve includes an oil suction valve seat (12), an oil suction valve spring (13), and an oil suction valve core (14). The oil suction valve seat (12) is fixedly installed inside the plunger (5) to provide a fixed support structure for the oil suction valve spring (13) and the oil suction valve core (14). The oil suction valve spring (13) is sleeved on the oil suction valve core (14). The drain valve includes a drain valve seat (9), a drain valve spring (10), and a drain valve core (11). The drain valve seat (9) is fixedly installed in the plunger hole to provide a fixed support structure for the drain valve spring (10) and the drain valve core (11). The drain valve spring (10) is sleeved on the drain valve core (11). The high-pressure valve distribution plunger pump is fixedly installed inside a sealed oil tank by bolts. The oil tank contains oil, and the oil in the oil tank enters the oil passage inside the high-pressure valve distribution plunger pump through the first through hole (18). An oil suction port is provided on the side wall of the plunger (5) away from the plunger cylinder (7).

2. The high-pressure valve distribution plunger pump according to claim 1, characterized in that, The end cap (1) is equipped with a lip seal (2) to prevent hydraulic oil leakage.

3. The high-pressure valve distribution plunger pump according to claim 1, characterized in that, A deep groove ball bearing (3) for supporting the rotational motion of the spindle swashplate (16) and a thrust bearing (4) for supporting the axial load of the spindle swashplate (16) are installed between the housing (17) and the spindle swashplate (16).

4. The high-pressure valve distribution plunger pump according to claim 1, characterized in that, One end of the plunger (5) is connected to the main shaft swashplate (16) via the plunger ball head (15) to realize the reciprocating motion of the plunger (5).

5. The high-pressure valve distribution plunger pump according to claim 1, characterized in that, The spindle swashplate (16) includes a spindle and a swashplate connected to each other, and the swashplate has an inclination angle in the radial direction.

6. The high-pressure valve distribution plunger pump according to claim 5, characterized in that, One end of the spindle extends out of the end cover (1), and the portion of the spindle extending out of the end cover (1) is connected to a drive mechanism for driving the spindle swashplate (16) to rotate.

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