A large displacement high-speed fuel plunger pump

Abstract

The application discloses a large-displacement high-speed fuel plunger pump and belongs to the technical field of hydraulic transmission and control, which comprises a shell and a main shaft, the main shaft is rotatably arranged in the shell, a cylinder body is arranged in the middle of the main shaft, sliding discs are arranged at the two ends of the main shaft, a plurality of plungers are arranged on the two sliding discs, a plurality of through plunger holes are formed in the cylinder body, and the extension ends of the plurality of plungers are slidably inserted into the plurality of plunger holes; a circular cavity is formed in the center of the sliding disc, a circlip groove and a slot-shaped sliding channel extending through the sliding disc are formed in the circular cavity, a disc circlip is embedded in the circlip groove, a pre-tightening disc is arranged in the circular cavity, and a disc spring is tightly arranged between the pre-tightening disc and the disc circlip; a ball hinge is further arranged on the main shaft through a cylindrical pin, and the outer side of the ball hinge penetrates through the pre-tightening disc and abuts against the disc spring. The application can improve the motion stability of the fuel plunger pump under high-speed and high-pressure working conditions, effectively reduce the abrasion caused by the direct contact between the plunger and the cylinder hole, and improve the displacement and unit power weight ratio of the plunger pump.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic transmission and control technology, and specifically relates to a large-displacement high-speed fuel plunger pump. Background Technology

[0002] Hypersonic vehicles have been a research hotspot for major aerospace powers worldwide for the past 20 years. Hypersonic vehicles will play an important strategic role in the future military, political and economic spheres, becoming a powerful tool for countries to seize strategic advantages in the air and space.

[0003] Fuel plunger pumps are core components of the fuel and control systems in hypersonic vehicle engines. Their performance directly affects the performance and reliability of the engine control system, and consequently, the performance and reliability of the hypersonic vehicle. As the Mach numbers of hypersonic vehicles increase, the fuel plunger pumps used in engines are required to possess ultra-high power density and operate with high reliability and efficiency. These stringent requirements pose significant challenges to the structure, materials, and manufacturing processes of existing plunger pumps.

[0004] However, due to structural limitations, existing fuel plunger pumps experience excessive centrifugal and lateral forces on the rotor assembly under ultra-high-speed conditions, causing the slipper assembly and cylinder block assembly to overturn. Furthermore, considering the influence of factors such as the low viscosity of aviation kerosene, the oil film bearing stability of the slipper pair and distribution pair is easily compromised, resulting in technical bottlenecks such as wear and burn-out of the slipper pair and distribution pair, increased leakage, reduced efficiency, and excessively high oil temperature.

[0005] The traditional distributed slipper pair structure is replaced by an integrated slipper pair structure. This structure not only increases the contact area of ​​the friction pair and effectively reduces the PV value of the friction pair, but also reduces leakage of the slipper pair. At the same time, the slipper pair structure, in conjunction with the conical plunger structure, can significantly reduce the lateral force of the plunger acting on the cylinder block. However, relying on the meshing contact between the conical plunger structure and the cylinder block to drive the cylinder block at high speed is prone to motion instability under high-speed and high-pressure conditions, as well as wear caused by the direct contact between the plunger and the cylinder bore. Summary of the Invention

[0006] The purpose of this invention is to provide a large-displacement, high-speed fuel plunger pump that not only improves the stability of the fuel plunger pump under high-speed and high-pressure conditions, but also effectively reduces the wear caused by direct contact between the plunger and the cylinder bore, thereby increasing the displacement and power-to-weight ratio of the plunger pump.

[0007] To achieve the objective of this invention, the technical solution adopted is as follows: A large-displacement high-speed fuel plunger pump includes a housing and a main shaft. The main shaft is rotatably installed inside the housing. A cylinder is installed in the middle of the main shaft, and sliding plates are installed at both ends of the main shaft. Multiple plungers are installed on each of the two sliding plates, and multiple through-holes are opened on the cylinder. The extension ends of the multiple plungers are slidably inserted into the multiple plunger holes. A circular cavity is opened in the center of the sliding plate. A retaining spring groove and a groove-shaped slide rail extending inward and penetrating to the inside of the sliding plate are opened in the circular cavity. A disc retaining spring is embedded in the retaining spring groove. A preload plate is installed in the circular cavity, and a disc spring is pressed between the preload plate and the disc retaining spring. A ball joint is also installed on the main shaft through a cylindrical pin. The end of the cylindrical pin is slidably inserted into the groove-shaped slide rail, and the outer side of the ball joint cooperates with the supporting spherical surface and presses against the disc spring.

[0008] Furthermore, a retaining ring is also fitted on the main shaft to abut against the inside of the ball joint.

[0009] Furthermore, a pressure plate is fixedly installed on the inner side of the slide plate to press the plunger end onto the slide plate, and the center of the pressure plate has a spherical surface corresponding to the circular cavity, and a strip groove corresponding to the grooved slide is opened on the spherical surface.

[0010] Furthermore, the outer casing includes a housing and an end cap. The two ends of the main shaft are rotatably supported on the housing and the end cap respectively by bearings. A distribution swashplate seat is installed inside the housing, with one slide plate supported on the distribution swashplate seat and the other slide plate supported on the end cap.

[0011] Furthermore, the end cap is provided with a low-pressure oil inlet and a high-pressure oil outlet, and the swash plate seat is provided with a swash plate seat suction port and a swash plate seat low-pressure distribution port. The two ends of the swash plate seat suction port are respectively connected to the inside of the housing and the swash plate seat low-pressure distribution port. The slide plate is also provided with a waist-shaped hole connecting the swash plate seat low-pressure distribution port to the inside of the plunger and the inside of the plunger to the high-pressure oil outlet.

[0012] Furthermore, the end cap is also provided with a connecting hole that connects the low-pressure oil inlet of the end cap to the inside of the outer casing.

[0013] Furthermore, the size of the low-pressure oil inlet of the end cap is larger than the size of the high-pressure oil outlet of the end cap.

[0014] Furthermore, the inner side of the distribution swash plate seat and the inner side of the end cover are provided with an outer sealing strip and an inner sealing strip. The outer sealing strip is located outside the low-pressure distribution port of the swash plate seat, and the inner sealing strip is located inside the low-pressure distribution port of the swash plate seat.

[0015] Furthermore, the slide plate is also provided with an outer sealing strip that seals with the outer sealing strip of the swash plate seat, and an inner sealing strip that seals with the inner sealing strip of the swash plate seat.

[0016] Furthermore, the oil suction port of the swash plate seat is located on the circumferential surface of the distribution swash plate seat, and both the oil suction port and the low-pressure distribution port of the swash plate seat are arc-shaped. The low-pressure distribution port of the swash plate seat is connected to multiple waist-shaped holes on the slide plate.

[0017] The beneficial effects of this invention are:

[0018] 1. This invention uses a cylindrical pin to mount a ball joint on the main shaft, so that the sliding plate and cylinder block can operate synchronously during the operation of the piston pump. This prevents the instability of the movement caused by contact between the piston and the piston hole under high-speed and high-pressure conditions, as well as the wear caused by direct contact between the piston and the piston hole.

[0019] 2. This invention partially separates and improves the centering, pre-tightening, supporting, and synchronizing functions of the slide and ball joint. Specifically, the pre-tightening function of the slide and ball joint is removed and indirectly transferred to the disc spring and pre-tightening plate. At the same time, the supporting conditions of the slide and ball joint are improved and simplified, thereby preventing problems such as severe wear and motion interference jamming caused by the four functions of the slide and ball joint being concentrated on the contact ball surface.

[0020] 3. By setting up two oil inlets, this invention significantly increases the oil volume without changing the size of the plunger pump, thereby improving the self-priming speed of the plunger pump and facilitating high-speed operation.

[0021] 4. In this invention, no lateral force is transmitted between the plunger and the cylinder, and the contact conditions of the three major friction pairs are significantly improved, which is beneficial for the reliable use of the plunger pump under high speed and high pressure.

[0022] 5. This invention can significantly increase the displacement of the fuel plunger pump, thereby further improving its power-to-weight ratio to meet the special requirements of aerospace. Attached Figure Description

[0023] The accompanying drawings illustrate exemplary embodiments of the invention and, together with the description thereof, serve to explain the principles of the invention. These drawings are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification.

[0024] Figure 1 A schematic diagram of the structure of the large-displacement high-speed fuel plunger pump provided by the present invention;

[0025] Figure 2 for Figure 1 Cross-sectional view of AA in the middle;

[0026] Figure 3 This is a diagram showing the internal oil flow of a large-displacement, high-speed fuel plunger pump.

[0027] Figure 4A schematic diagram showing the installation of the disc retainer, disc spring, and preload disc on the slide plate;

[0028] Figure 5 This is a cross-sectional view of the slider;

[0029] Figure 6 This is the right view of the slider;

[0030] Figure 7 This is a surface structure diagram of the swashplate holder;

[0031] Figure 8 This is a side view of the distribution swashplate.

[0032] The attached diagram shows the markings and corresponding component names:

[0033] 1. Housing, 2. Swashplate seat, 3. Sliding plate, 4. Pressure plate, 5. Plunger, 6. Ball joint, 7. Cylinder block, 8. End cover, 9. Bearing, 10. Swashplate seat bolt, 11. Disc circlip, 12. Disc spring, 13. Preload disc, 14. Cylindrical pin, 15. Fastening bolt, 16. Shaft circlip, 17. Cylinder block circlip, 18. Swashplate seat oil suction port, 19. Waist-shaped hole, 20. Center hole, 21. Cavity, 22. Plunger hole, 23. End cover high-pressure distribution. 24. High-pressure oil outlet of end cover; 25. Low-pressure oil inlet of end cover; 26. Connecting hole; 27. Low-pressure distribution port of end cover; 28. External sealing strip of sliding plate; 29. ​​Internal sealing strip of sliding plate; 30. Snap ring groove; 31. Circular cavity; 32. Ball socket; 33. Groove slide; 34. Connecting hole; 35. Support spherical surface; 36. Low-pressure distribution port of swashplate seat; 37. External sealing strip of swashplate seat; 38. Internal sealing strip of swashplate seat; 39. Bolt hole; 40. Main shaft. Detailed Implementation

[0034] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for illustrative purposes only and are not intended to limit the scope of the invention. Furthermore, it should be noted that, for ease of description, only the parts relevant to the present invention are shown in the accompanying drawings.

[0035] It should be noted that, unless otherwise specified, the embodiments and features described in this invention can be combined with each other. The invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0036] like Figure 1 , Figure 2 , Figure 3As shown, the present invention provides a large-displacement high-speed fuel plunger pump, comprising a housing and a main shaft 40. The central axis of the main shaft 40 is collinear with the central axis of the housing, and both ends of the main shaft 40 are rotatably mounted on the housing. One end of the main shaft 40 can extend outward through the housing. A cylinder 7 is mounted in the middle of the main shaft 40, and the central axis of the cylinder 7 is collinear with the central axis of the main shaft 40. The cylinder 7 has multiple plunger holes 22, typically 7, 9, or 11. The two ends of each plunger hole 22 penetrate both ends of the cylinder 7, and the multiple plunger holes 22 are evenly spaced along the circumference of the cylinder 7. Sliding discs 3 are also mounted at both ends of the main shaft 40, and the two sliding discs 3 are symmetrical on both sides of the cylinder 7. The slide plate 3 has multiple ball sockets 32, the number of which is equal to the number of plunger holes 22, and each ball socket 32 ​​corresponds to a plunger hole 22. A plunger 5 is installed in each of the ball sockets 32. The plunger 5 has a large-diameter ball end and a small-diameter ball end, with a tapered configuration between the large-diameter and small-diameter ball ends. The plunger 5 has a central hole 20 for oil inlet and outlet. The large-diameter ball end of the plunger 5 is installed in the ball socket 32, allowing the plunger 5 to swing freely on the slide plate 3. The diameter of the small-diameter ball end of the plunger 5 matches the diameter of the plunger hole 22, and the small-diameter ball end of the plunger 5 is slidably installed in the corresponding plunger hole 22, allowing the small-diameter ball end of the plunger 5 to reciprocate within the plunger hole 22. Since both ends of the spindle 40 are provided with slides 3, and both slides 3 are equipped with plungers 5, the ball head of the plunger 5 on one slide 3 is slidably installed at one end of the plunger hole 22, and the ball head of the plunger 5 on the other slide 3 is slidably installed at the other end of the plunger hole 22. At the same time, since the plunger 5 has a central hole 20 inside, and the two ends of the central hole 20 pass through the two ends of the plunger 5, when the ball heads of the two plungers 5 are slidably installed at the two ends of the plunger hole 22, the central holes 20 inside the two plungers 5 can be connected through the plunger hole 22.

[0037] like Figure 4 , Figure 5 , Figure 6As shown, the slide plate 3 has a circular cavity 31 at its center, giving it a through-hole structure. The slide plate 3 is fitted onto the main shaft 40 through the circular cavity 31. A snap ring groove 30 is provided inside the circular cavity 31. The snap ring groove 30 is an annular groove, and its diameter direction is consistent with that of the circular cavity 31. The snap ring groove 30 is located at one end of the circular cavity 31 closest to the slide plate 3. At the same time, a grooved slide 33 is also provided inside the circular cavity 31. The axis of the grooved slide 33 is consistent with the length direction of the circular cavity 31, and one end of the grooved slide 33 penetrates the inner side of the slide plate 3. The other end of the grooved slide 33 is spaced apart from the snap ring groove 30. A disc retaining spring 11 is embedded in the retaining spring groove 30, and a preload disc 13 is installed in the circular cavity 31. A disc spring 12 is pressed between the preload disc 13 and the disc retaining spring 11. A ball joint 6 is also installed on the main shaft 40 via a cylindrical pin 14. Both ends of the cylindrical pin 14 extend outward through the ball joint 6 into the grooved slide 33 and slide in cooperation with the grooved slide 33, so that both ends of the cylindrical pin 14 can slide along the grooved slide 33, allowing the main shaft 40 to pass through the grooved slide 33 when rotating. The pin 14 drives the slide plate 3 to move synchronously; at the same time, both sides of the ball joint 6 are flat, and the circumferential surface of the ball joint 6 is spherical. When the ball joint 6 is installed, the outer end face of the ball joint 6 is pressed against the disc spring 12, and the center of the preload plate 13 has a supporting spherical surface 35 that mates with the circumferential surface of the ball joint 6. After the ball joint 6 is installed, the circumferential surface of the ball joint 6 slides in contact with the supporting spherical surface 35 on the preload plate 13, so that the ball joint 6 can swing relative to the preload plate 13, thereby allowing the spindle 40 to rotate freely.

[0038] like Figure 1 As shown, the main shaft 40 is also provided with two shaft retaining rings 16. The two shaft retaining rings 16 are located inside the two ball joints 6 respectively, and the two shaft retaining rings 16 respectively abut and restrict the inner side of the two ball joints 6. Through the cooperation of the shaft retaining rings 16, disc retaining rings 11, disc springs 12 and preload discs 13, the ball joints 6 are installed and the disc springs 12 can maintain a certain preload after the shaft retaining rings 16 are installed, so that the position of the sliding plate 3 is more stable and prevents oil leakage during the initial operation of the plunger pump.

[0039] The inner side of the slide plate 3 is also provided with a pressure plate 4, and the slide plate 3 is also provided with a connecting hole 34. When the pressure plate 4 is installed, the fastening bolt 15 passes through the connecting hole 34 and locks with the pressure plate 4, so that the pressure plate 4 and the slide plate 3 are fixedly connected by the fastening bolt 15. At the same time, the pressure plate 4 has a spherical surface corresponding to the ball socket 32 ​​on the slide plate 3. Through the cooperation of the spherical surface on the pressure plate 4 and the ball socket 32 ​​on the slide plate 3, the depth of the ball socket 32 ​​for installing the large diameter ball end of the plunger 5 is greater than half the diameter of the large diameter ball end of the plunger 5, so that the large diameter ball end of the plunger 5 will not fall off after being installed in the ball socket 32. At the same time, in order to facilitate the smooth sliding of both ends of the cylindrical pin 14 in the grooved slide 33, the center of the pressure plate 4 is also provided with a through hole corresponding to the circular cavity 31, and a strip groove corresponding to the grooved slide 33 is opened on the through hole.

[0040] The outer casing includes a housing 1 and an end cover 8. The end cover 8 is bolted to the housing 1 to maintain a sealed interior. Bearings 9 are installed on both the housing 1 and the end cover 8. One end of the main shaft 40 is rotatably supported on the housing 1 via the bearing 9, and the other end of the main shaft 40 is rotatably supported on the end cover 8 via the bearing 9. A swashplate seat 2 is also installed inside the housing 1. One sliding plate 3 is supported on the swashplate seat 2 and slides in contact with it, while another sliding plate 3 is supported on the end cover 8 and slides in contact with it. By ensuring a tight seal between one sliding plate 3 and the swashplate seat 2, and between the other sliding plate 3 and the end cover 8, oil leakage during the initial operation of the plunger pump can be effectively prevented.

[0041] like Figure 2 , Figure 3 As shown, the end cap 8 has a low-pressure oil inlet 25 and a high-pressure oil outlet 24. The outlet end of the low-pressure oil inlet 25 is the high-pressure distribution port 23, and the inlet end of the high-pressure oil outlet 24 is the low-pressure distribution port 27. Simultaneously, the swash plate seat 2 has a swash plate seat suction port 18 and a swash plate seat low-pressure distribution port 36. One end of the swash plate seat suction port 18 communicates with the interior of the housing 1, and the other end communicates with the swash plate seat low-pressure distribution port 36. Both sliding plates 3 are provided with oblong holes 19, the number of which is equal to the number of plungers 5 on the sliding plate 3. When the plungers 5 are installed, the oblong holes 19 communicate with the center holes 20 on the plungers 5. Since one slide plate 3 is directly and tightly attached to the end cover 8, and the other slide plate 3 is tightly attached to the distribution swashplate seat 2, after the two slide plates 3 are installed, the other end of the waist-shaped hole 19 on the slide plate 3 that is tightly attached to the end cover 8 is connected to the high-pressure distribution port 23 on the end cover 8; the other end of the waist-shaped hole 19 on the slide plate 3 that is tightly attached to the distribution swashplate seat 2 is connected to the low-pressure distribution port 36 on the distribution swashplate seat 2.

[0042] The end cap 8 is also provided with a connecting hole 26. One end of the connecting hole 26 is connected to the low-pressure oil inlet 25 of the end cap, and the other end of the connecting hole 26 is connected to the cavity 21 inside the housing, so that the low-pressure oil can enter the housing 1 through the low-pressure oil inlet 25 of the end cap. The size of the low-pressure oil inlet 25 of the end cap 8 is larger than the size of the high-pressure oil outlet 24 of the end cap.

[0043] The distribution swash plate seat 2 is provided with bolt holes 39. When installing the distribution swash plate seat 2, swash plate seat bolts 10 are installed on the housing 1 and the swash plate seat bolts 10 are tightened and fixed in the bolt holes 39, thereby fixing the distribution swash plate seat 2 to the housing 1 and realizing the fixed installation of the distribution swash plate seat 2.

[0044] like Figure 7 As shown, the inner side of the distribution swash plate seat 2 and the inner side of the end cover 8 are provided with an outer sealing strip 37 and an inner sealing strip 38. The inner side of the distribution swash plate seat 2 is the side where the distribution swash plate seat 2 slides with the slide plate 3, and the inner side of the end cover 8 is the side where the end cover 8 slides with the slide plate. The inner sealing strip 38 and the outer sealing strip 37 of the swash plate seat are arranged from the inside to the outside along the radial direction of the distribution swash plate seat 2. Specifically, the outer sealing strip 37 of the swash plate seat is located outside the low-pressure distribution port 36 of the swash plate seat, and the inner sealing strip 38 of the swash plate seat is located inside the low-pressure distribution port 36 of the swash plate seat.

[0045] The slide plate 3 is also provided with an outer sealing strip 28 that seals with the outer sealing strip 37 of the swash plate seat and an inner sealing strip 29 that seals with the inner sealing strip 38 of the swash plate seat. That is, the outer sealing strip 28 and the inner sealing strip 29 are both located on the outer surface of the slide plate 3, and the inner sealing strip 29 and the outer sealing strip 28 are arranged from the inside to the outside along the radial direction of the slide plate 3.

[0046] like Figure 8 As shown, the oil suction port 18 of the swash plate seat is located on the circumferential surface of the distribution swash plate seat 2, and both the oil suction port 18 and the low-pressure distribution port 36 of the swash plate seat are arc-shaped. The low-pressure distribution port 36 of the swash plate seat is connected to multiple waist-shaped holes 19 on the slide plate 3, making the structure of the distribution swash plate seat 2 simpler.

[0047] To ensure the stability of the cylinder body 7 mounted on the main shaft 40, the cylinder body 7 and the main shaft 40 are connected by a spline, so that the main shaft 40 rotates while driving the cylinder body 7 to rotate synchronously; at the same time, in order to prevent the cylinder body 7 from moving axially on the main shaft 40, the main shaft 40 is also equipped with cylinder body 7 retaining springs that abut against both sides of the cylinder body 7 respectively.

[0048] like Figure 3As shown, during the operation of the plunger pump, when suctioning oil, low-pressure oil enters from the low-pressure oil inlet 25 on the end cover 8 and enters the plunger hole 22 of the cylinder 7 in two paths. One path enters the plunger hole 22 through the low-pressure distribution port 27 on the end cover, the waist-shaped hole 19, and the center hole 20 on the plunger 5. The other path enters the plunger hole 22 through the low-pressure distribution port 27 on the end cover, the connecting hole 26, the cavity 21 inside the housing 1, the oil suction port of the distribution swashplate seat 2, the waist-shaped hole 19, and the center hole 20 on the plunger 5. When pumping oil, high-pressure oil is discharged from the plunger hole 22 through the center hole 20, the waist-shaped hole 19, the high-pressure distribution port 23 on the end cover, and the high-pressure oil outlet in sequence.

[0049] The piston pump provided by this invention is improved in two main aspects: First, the preload action between the sliding plate 3 and the ball joint 6 is separated, that is, the preload action between the sliding plate 3 and the ball joint 6 is indirectly transferred to the disc spring 12 and the preload plate 13, and the preload plate 13 and the ball joint 6 achieve a sliding fit through the supporting spherical surface 35. Second, the support conditions between the sliding plate 3 and the ball joint 6 are improved, that is, the contact between the sliding plate 3 and the ball joint 6 is changed from the traditional spherical support to the line support, which simplifies the relationship between the two and reduces the problems of motion interference and wear jamming caused by excessive constraints of spherical contact, thereby enabling the piston pump to operate under ultra-high speed conditions.

[0050] Therefore, as can be seen from the above description, to achieve normal operation of a high-speed plunger pump, the following four functions exist directly or indirectly between the sliding disc 3 and the ball joint 6: centering, pre-tightening, supporting, and synchronizing. Centering means that the swing center of the sliding disc 3 must be aligned with the center of the ball joint 6. Pre-tightening means that a certain initial pre-tightening force must be ensured when the sliding disc 3 abuts against the end cover 8 or the distribution swashplate seat 2. Supporting means that the sliding disc 3 needs support to operate stably. Synchronizing means that the sliding disc 3 and the cylinder block 7 must operate synchronously. In the existing technology, these four functions are generally concentrated on the contact surface between the sliding disc 3 and the ball joint 6, meaning that all four functions are concentrated on the contact surface. Therefore, the motion and force relationships of the contact surface between the sliding disc 3 and the ball joint 6 are very complex, requiring high machining and assembly precision. Furthermore, these four functions are interconnected and mutually influential, easily causing motion interference, severe wear on the surface of the ball joint 6 and the contact area between the cylindrical pin 14 and the grooved slide 33, leading to motion jamming and inability to operate at high speed.

[0051] In the description of this specification, the references to terms such as "one embodiment / mode," "some embodiments / modes," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment / mode or example is included in at least one embodiment / mode or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment / mode or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments / modes or examples. Furthermore, without contradiction, those skilled in the art can combine and integrate the different embodiments / modes or examples described in this specification, as well as the features of different embodiments / modes or examples.

[0052] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0053] Those skilled in the art should understand that the above embodiments are merely for illustrating the present invention and are not intended to limit the scope of the invention. Those skilled in the art can make other changes or modifications based on the above disclosure, and these changes or modifications still fall within the scope of the present invention.

Claims

1. A large-displacement, high-speed fuel plunger pump, characterized in that, The assembly includes a housing and a main shaft (40). The main shaft (40) is rotatably mounted inside the housing. A cylinder (7) is mounted in the middle of the main shaft (40). Slides (3) are mounted at both ends of the main shaft (40). Multiple plungers (5) are mounted on each of the two slides (3). Multiple through plunger holes (22) are provided on the cylinder (7). The extension ends of the multiple plungers (5) are slidably inserted into the multiple plunger holes (22). A circular cavity (31) is provided in the center of the slide (3). A snap ring groove (30) and a groove extending through the inner side of the slide (3) are provided in the circular cavity (31). The slide (33) has a disc retainer (11) embedded in the retainer groove (30), and a preload disc (13) is installed in the circular cavity (31). The preload disc (13) has a supporting spherical surface (35) at its center, and a disc spring (12) is pressed between the preload disc (13) and the disc retainer (11). A ball joint (6) is also installed on the main shaft (40) through a cylindrical pin (14). A shaft retainer (16) is also embedded on the main shaft (40) and presses against the inner side of the ball joint (6). The end of the cylindrical pin (14) is slidably inserted into the grooved slide (33), and the outer side of the ball joint (6) is flush with the supporting spherical surface. (35) Cooperate and press the disc spring (12); the inner side of the slide (3) is also fixedly installed with a pressure plate (4) that presses the end of the plunger (5) onto the slide (3), and the center of the pressure plate (4) has a spherical surface corresponding to the circular cavity (31), and a strip groove corresponding to the grooved slide (33) is opened on the spherical surface; the outer shell includes a shell (1) and an end cover (8), the two ends of the main shaft (40) are rotatably supported on the shell (1) and the end cover (8) respectively by bearings (9), and a distribution swashplate seat (2) is installed in the shell (1), and a slide (3) is supported on the distribution swashplate seat (2). 2) On the other side, another slide (3) is supported on the end cover (8); the end cover (8) is provided with an end cover low pressure oil inlet (25) and an end cover high pressure oil outlet (24), the distribution swash plate seat (2) is provided with a swash plate seat suction port (18) and a swash plate seat low pressure distribution port (36), the two ends of the swash plate seat suction port (18) are respectively connected to the inside of the housing (1) and the swash plate seat low pressure distribution port (36), and the slide (3) is also provided with a waist-shaped hole (19) connecting the swash plate seat low pressure distribution port (36) with the inside of the plunger (5) and the inside of the plunger (5) with the end cover high pressure oil outlet (24).

2. The large-displacement high-speed fuel plunger pump according to claim 1, characterized in that, The end cap (8) is also provided with a connecting hole (26) that connects the low-pressure oil inlet (25) of the end cap to the inside of the outer shell.

3. The large-displacement high-speed fuel plunger pump according to claim 1, characterized in that, The size of the low-pressure oil inlet (25) of the end cap is larger than the size of the high-pressure oil outlet (24) of the end cap.

4. The large-displacement high-speed fuel plunger pump according to claim 1, characterized in that, The inner side of the distribution swash plate seat (2) and the inner side of the end cover (8) are provided with an outer sealing strip (37) and an inner sealing strip (38). The outer sealing strip (37) is located outside the low-pressure distribution port (36) of the swash plate seat, and the inner sealing strip (38) is located inside the low-pressure distribution port (36) of the swash plate seat.

5. The large-displacement high-speed fuel plunger pump according to claim 4, characterized in that, The slide plate (3) is also provided with an outer sealing strip (28) that seals with the outer sealing strip (37) of the swash plate seat and an inner sealing strip (29) that seals with the inner sealing strip (38) of the swash plate seat.

6. The large-displacement high-speed fuel plunger pump according to claim 1, characterized in that, The oil suction port (18) of the swash plate seat is located on the circumferential surface of the distribution swash plate seat (2), and both the oil suction port (18) and the low-pressure distribution port (36) of the swash plate seat are arc-shaped. The low-pressure distribution port (36) of the swash plate seat is connected to multiple waist-shaped holes (19) on the slide plate (3).

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