A double-cylinder inclined-opposed V-type plunger pump

Abstract

This invention provides a dual-cylinder tilted opposed V-type plunger pump, belonging to the field of plunger pump technology. It solves the problem of how to maintain good working performance of a plunger pump after long-term operation. This dual-cylinder tilted opposed V-type plunger pump includes a housing, two cylinders, and a main shaft. Each cylinder is a disc-shaped component with an axial mounting hole in the center. The two cylinders are respectively fitted onto the main shaft through their respective mounting holes and rotate synchronously with the main shaft. The axes of both cylinders are tilted relative to the main shaft, and the two cylinders are arranged symmetrically in a V-shape. Several plunger holes are arranged circumferentially on the cylinders, with the axes of the plunger holes parallel to the axes of the cylinders. A cylindrical plunger, coaxial with the plunger hole, slides within each plunger hole, with the outer end of each plunger extending out of the plunger hole. The plungers on the two cylinders are arranged opposite each other, and the outer ends of the two opposing plungers are hinged together. This invention ensures that the plunger pump maintains good working performance over a long period.

Description

Technical Field

[0001] This invention belongs to the field of plunger pump technology and relates to a dual-cylinder tilted opposed V-type plunger pump. Background Technology

[0002] Piston pumps are core power components of hydraulic systems, widely used in engineering machinery, aerospace equipment, and industrial hydraulic equipment due to their advantages of high pressure and high power density. A conventional axial piston pump mainly consists of a housing, main shaft, cylinder block, distributor plate, swashplate, and piston assembly. The cylinder block rotates synchronously with the main shaft, and the piston reciprocates within the piston bore of the cylinder block. This, combined with the waist-shaped flow channel of the distributor plate, enables the alternating conduction of high and low pressure oil, completing the oil suction and discharge cycle, thereby outputting continuous pressurized oil.

[0003] Existing plunger pump structures, such as the floating swashplate axial plunger pump with a symmetrical tilting rotating assembly disclosed in patent literature (application number: 202311632522.9), include a pump body, a main shaft installed in the pump body, a turntable installed on the main shaft, and an equal number of ball sockets symmetrically provided on both sides of the turntable. Ball joints are splined or integrally formed on both sides of the turntable on the main shaft. A cylinder is installed on the outside of each ball joint. Multiple cylinder holes are provided on the side of each cylinder near the turntable, with each cylinder hole corresponding to a ball socket. A thin rod plunger is provided in each cylinder hole, with the end of the thin rod plunger extending out of the cylinder hole and into the ball socket of the corresponding turntable.

[0004] The plunger pump has the following shortcomings in actual use:

[0005] 1. This plunger pump uses a ball socket on a rotary table to engage with the ball head on the end face of a thin rod plunger, allowing the thin rod plunger to extend and retract within the plunger bore as the rotary table rotates circumferentially. Because the rotary table is rigidly fixed to the main shaft, the thin rod plunger is continuously subjected to external forces from the rotary table as it rotates with the main shaft. This causes continuous sliding friction between the plunger ball head and the ball socket, leading to severe wear of the thin rod plunger and consequently, a decrease in pump performance.

[0006] 2. In this plunger pump, the thin rod plunger and the plunger bore are not coaxially aligned. During its revolution, the thin rod plunger needs to extend and retract along the plunger bore while also continuously tilting and oscillating relative to the cylinder block. Therefore, the thin rod plunger and the plunger bore use a line seal contact, resulting in a small effective sealing contact area. During long-term continuous operation, the contact area between the thin rod plunger and the plunger bore will continuously wear down. Furthermore, the enormous hydraulic pressure of the high-pressure oil will concentrate in the small line contact area, leading to poor sealing and medium leakage in the contact area after prolonged operation. This, in turn, causes a continuous decrease in the volumetric efficiency of the plunger pump and insufficient output pressure. Therefore, this plunger pump has a problem in guaranteeing its performance after long-term operation. Summary of the Invention

[0007] The purpose of this invention is to address the aforementioned problems in existing technologies by proposing a dual-cylinder tilting opposed V-type piston pump. The technical problem solved by this invention is: how to ensure that the piston pump maintains good working performance after long-term operation.

[0008] The objective of this invention can be achieved through the following technical solution: A dual-cylinder tilting opposed V-type plunger pump, comprising a housing, two cylinders, and a main shaft rotatably disposed within the housing. Each cylinder is a disc-shaped component with an axial mounting hole in the center. The two cylinders are respectively fitted onto the main shaft through their respective mounting holes and rotate synchronously with the main shaft. The axial directions of the two cylinders are tilted relative to the main shaft, and the two cylinders are arranged symmetrically in a V-shape. A plurality of plunger holes are arranged sequentially along the circumference on the cylinder. The characteristic feature is that the axial direction of the plunger holes is parallel to the axial direction of the cylinders. A cylindrical plunger coaxial with the plunger hole is slidably disposed in each plunger hole, and the outer end of each plunger extends out of the plunger hole. The plungers on the two cylinders are arranged facing each other, and the outer ends of the two opposing plungers are hinged together.

[0009] When the spindle rotates, the cylinder block rotates synchronously with the spindle, and the plungers on the cylinder block revolve around the spindle. Since the axes of the two cylinder blocks are inclined relative to the spindle and are arranged symmetrically in a V-shape, the plungers will reciprocate along the plunger holes in the cylinder block during the revolution, thereby completing the oil suction and discharge, allowing the plunger pump to continuously output pressurized oil.

[0010] This plunger pump uses a cylindrical plunger that slides coaxially within the plunger bore, with the bore axis parallel to the cylinder axis. This structure ensures that while the cylinder revolves with the main shaft, the plunger only revolves around the main shaft, preventing tilting or wobbling relative to the plunger bore. Therefore, the plunger and plunger bore maintain constant surface contact, significantly increasing the sealing area and improving sealing performance. Furthermore, the high-pressure oil load is evenly distributed across the entire cylindrical mating surface, resulting in lower pressure per unit area. This effectively reduces the wear rate of the plunger-plunger mating surface, minimizing media leakage during long-term operation and thus stabilizing volumetric efficiency and output pressure.

[0011] However, when the plunger is in contact with the plunger bore surface, a high degree of coaxial fit precision is required. Machining or assembly deviations can easily lead to plunger jamming and accelerated localized wear. To address this, this plunger pump hinges the outer ends of two opposing plungers to form a floating connection structure. This adaptively compensates for machining and assembly errors, allowing the plunger to automatically align within the plunger bore and ensuring a consistently high degree of coaxiality. Furthermore, this structure eliminates the need for an integrated spindle turntable to drive the plunger's reciprocating motion. Therefore, the plunger does not bear the force exerted by the turntable, completely eliminating wear between the turntable ball joint and the plunger ball head, ensuring the plunger pump maintains excellent long-term performance.

[0012] In the aforementioned twin-cylinder tilting opposed V-type piston pump, the two opposing pistons are hinged together by pins. Each pin is located on the symmetrical plane of the two cylinders, and the axis of each pin is perpendicular to the plane where the axes of the corresponding two pistons lie. This hinged structure allows the pistons to adaptively adjust their angles by slightly deflecting around the pins during reciprocating extension and retraction along the piston bore. This prevents the pistons from jamming due to uneven force, ensuring that the pistons can always slide smoothly coaxially with the piston bore. This further reduces the wear rate between the pistons and the piston bore during long-term operation, thereby ensuring that the piston pump maintains good working performance over a long period.

[0013] In the aforementioned twin-cylinder tilting opposed V-type plunger pump, of the two opposing plungers, one plunger has two axially protruding, plate-like hinged protrusions at its outer end, and the other plunger has an axially protruding, plate-like hinged protrusion at its middle outer end. The hinged protrusions are embedded between the two hinged protrusions, and a pin perpendicularly penetrates both hinged protrusions. This structure not only facilitates assembly and manufacturing, but also prevents the plungers from circumferentially twisting around their own axis by arranging the hinged protrusions on either side of the hinged protrusions, thus avoiding problems such as localized wear and seal failure caused by plunger torsion.

[0014] In the aforementioned twin-cylinder tilting opposed V-type plunger pump, the plunger has an axially extending bore penetrating its inner end face, and this bore is filled with low-density packing. The low-density packing effectively reduces the overall weight of the plunger. When the plunger reciprocates with the spindle, the centrifugal inertia generated by the plunger is smaller, reducing the contact pressure between the plunger and the inner wall of the plunger bore during high-speed operation. This further reduces wear between the plunger and the plunger bore, ensuring the fitting accuracy between the plunger and the plunger bore during long-term operation. In actual manufacturing, the low-density packing can be a lightweight alloy or engineering plastic.

[0015] In the aforementioned dual-cylinder tilted opposed V-type plunger pump, two swashplates are fixedly installed inside the housing, each located outside one of the two cylinders. The inner surface of each swashplate is parallel and directly opposite the outer end face of the cylinder on the same side. A distribution plate is provided between each swashplate and the cylinder on the same side, and the distribution plate is fixedly connected to the swashplate and fits against the outer end face of the cylinder. In this structure, the swashplate provides stable rigid support for the distribution plate, ensuring a stable fit between the distribution plate and the cylinder end face, reducing cross-flow of high and low pressure oil, and stabilizing pump volumetric efficiency. In actual manufacturing, several oil passage holes are spaced around the main shaft axis on the swashplate. Each plunger hole penetrates the cylinder end face near the distribution plate, so that as the cylinder rotates with the main shaft, each plunger hole alternately connects with the oil passage hole, thereby coordinating with the extension and retraction of the plunger to complete oil suction and discharge.

[0016] In the aforementioned twin-cylinder tilting opposed V-type plunger pump, the swashplate has an inwardly extending annular flange along its circumferential edge, and the outer circumferential surface of the cylinder body abuts against the inner circumferential surface of the annular flange. The annular flange provides radial limiting and guiding for the cylinder body, restricting radial displacement during operation and ensuring stable cylinder rotation. This prevents cylinder body wobbling that could lead to uneven wear between the plunger and the plunger bore, further improving the long-term stability of the plunger pump. Additionally, the annular flange provides a sealed protection around the cylinder body, reducing oil leakage and enhancing the pump's performance.

[0017] In the aforementioned dual-cylinder tilted opposed V-type piston pump, two annular protrusions are formed on the outer wall of the main shaft, spaced apart along the axial direction. Each annular protrusion is circumferentially arranged along the main shaft and has a spherical surface. The two cylinders are fitted onto the two annular protrusions one-to-one. The spherical surface of the annular protrusions allows them to fit the tilted cylinders. During assembly, the cylinders can adjust their fit position after being fitted onto the spherical annular protrusions, reducing alignment difficulty and making assembly more convenient. At the same time, it ensures that the outer end face of the cylinder fits well with the distribution plate, preventing cross-flow of high and low pressure oil and stabilizing the pump's volumetric efficiency.

[0018] In the aforementioned twin-cylinder tilting opposed V-type plunger pump, the outer end of the mounting hole is a stepped section with an increased radial dimension. The stepped section transitions to the small-diameter section of the mounting hole via an annular stepped surface. A retaining ring is fixedly embedded on the inner circumferential wall of the stepped section. Each annular protrusion of the main shaft is fitted with a support ring that abuts against the stepped surface, and the inner circumferential surface of the support ring slides in contact with the annular protrusion. A corrugated gasket with a circumferentially wavy shape is sandwiched between the retaining ring and the adjacent support ring. In this structure, the corrugated gasket pushes the support ring, causing it to abut against the stepped surface and thus positioning the support ring. At this time, because the inner circumferential surface of the support ring slides in contact with the annular protrusion, the annular protrusion forms a rigid fulcrum, causing the corrugated gasket to exert a reverse pushing force on the retaining ring, thereby pressing the cylinder block tightly against the distributor plate. This prevents the gap from widening and high / low pressure oil leakage, ensuring the working performance of the plunger pump.

[0019] In the aforementioned twin-cylinder tilting opposed V-type piston pump, each annular protrusion has several cylindrical protrusions spaced circumferentially along the main shaft. Several circumferentially spaced grooves are formed on the inner circumferential wall of the cylinder mounting hole. These grooves are straight and parallel to the cylinder axis, and the protrusions are correspondingly embedded in each groove. The protrusions embedded in the grooves achieve circumferential positioning of the main shaft and the cylinder, and the torque transmitted by the protrusions drives the cylinder to rotate synchronously with the main shaft. During installation, after the cylinder is fitted onto the main shaft, the tilt angle can be adjusted along the spherical surface of the annular protrusion. The protrusions will then slide within the straight grooves until the cylinder is properly installed, thus facilitating installation.

[0020] In the aforementioned twin-cylinder tilting opposed V-type piston pump, the diameter of the protrusion matches the width of the groove. This structure ensures that the cylinder always rotates synchronously with the spindle, resulting in stable long-term operation of the piston pump.

[0021] In the aforementioned twin-cylinder tilted opposed V-type plunger pump, several plunger holes are arranged in two concentric rings on the cylinder block, with an equal number of holes in both rings. The plunger holes in each ring are evenly spaced along the circumference of the cylinder block, while the plunger holes in the inner and outer rings are staggered radially. If a conventional single-ring plunger hole design is used, the gaps between adjacent plunger holes prevent continuous connection of their effective oil discharge ranges, easily leading to flow peak-to-valley differences and noticeable pulsation. This plunger pump employs a two-ring plunger hole design with staggered arrangement, ensuring that the gaps between adjacent plunger holes in the inner and outer rings are radially opposite. When the oil discharge from the outer ring plunger holes reaches a low point, it is compensated for by the oil discharge from the inner ring plunger holes, resulting in a more stable total output flow, significantly reducing flow and pressure pulsation, and improving the pump's operational stability.

[0022] Compared with existing technologies, this dual-cylinder tilting opposed V-type piston pump has the following advantages:

[0023] 1. This plunger pump uses a cylindrical plunger that slides coaxially within the plunger bore. The plunger and bore are always in surface contact, significantly increasing the sealing area and improving sealing performance. Furthermore, the high-pressure oil load is evenly distributed across the entire cylindrical mating surface, resulting in lower pressure per unit area. This effectively reduces the wear rate of the plunger-bore mating surface, minimizing media leakage during long-term operation and thus stabilizing volumetric efficiency and output pressure.

[0024] 2. This plunger pump achieves the reciprocating extension and retraction of the plunger within the plunger bore by hinged connection of the plunger ends. This structure no longer relies on the external force applied by the integrated spindle turntable to drive the plunger reciprocating motion. Therefore, the plunger does not need to bear the external force applied to it by the turntable, thus completely eliminating the wear between the turntable ball socket and the plunger ball head, ensuring that the plunger pump maintains good working performance for a long time. Attached Figure Description

[0025] Figure 1 This is a three-dimensional structural diagram of the plunger pump.

[0026] Figure 2 This is a top view of the plunger pump.

[0027] Figure 3 yes Figure 2 Sectional view of AA.

[0028] Figure 4 This is a schematic diagram of the internal structure of this plunger pump.

[0029] Figure 5 This is an exploded view of the internal structure of this plunger pump.

[0030] Figure 6 It is an exploded view of the cylinder block and plunger.

[0031] Figure 7 This is a schematic diagram of the plunger connection structure.

[0032] Figure 8 This is an exploded view of the plunger connection structure.

[0033] Figure 9 This is a partial sectional view of the plunger pump.

[0034] Figure 10 This is a side view of the plunger pump.

[0035] Figure 11 yes Figure 10 Sectional view of AA.

[0036] Figure 12 This is a schematic diagram of the three-dimensional structure of the main shaft.

[0037] Figure 13 This is a partial structural schematic diagram of Embodiment 2 of this plunger pump.

[0038] Figure 14 This is a three-dimensional structural diagram of the cylinder block in Embodiment 2 of this plunger pump.

[0039] In the diagram, 1. Housing; 2. Cylinder block; 21. Mounting hole; 211. Stepped hole section; 212. Stepped surface; 22. Plunger hole; 23. Groove; 3. Main shaft; 31. Annular protrusion; 32. Protruding post; 4. Plunger; 41. Hinge protrusion one; 42. Hinge protrusion two; 43. Hole; 5. Pin; 6. Low-density packing; 7. Swashplate; 71. Annular flange; 8. Distribution plate; 81. Oil passage hole; 9. Retaining ring; 10. Support ring; 11. Corrugated gasket. Detailed Implementation

[0040] The following are specific embodiments of the present invention, which are described in conjunction with the accompanying drawings. However, the present invention is not limited to these embodiments.

[0041] Example 1

[0042] like Figures 1 to 3As shown, this dual-cylinder tilting opposed V-type plunger pump includes a housing 1, two cylinders 2, and a main shaft 3 rotatably mounted within the housing 1. Each cylinder 2 is a disc-shaped component with an axial mounting hole 21 in its center. The two cylinders 2 are respectively mounted on the main shaft 3 through their respective mounting holes 21 and rotate synchronously with the main shaft 3. The axes of both cylinders 2 are tilted relative to the main shaft 3, and the two cylinders 2 are arranged symmetrically in a V-shape. Several plunger holes 22 are sequentially arranged circumferentially on each cylinder 2. The axes of the plunger holes 22 are parallel to the axes of the cylinders 2. Figure 3 and Figure 4 As shown, a cylindrical plunger 4 coaxial with the plunger hole 22 is slidably disposed in each plunger hole 22. The outer end of each plunger 4 extends out of the plunger hole 22. The plungers 4 on the two cylinder bodies 2 are arranged facing each other, and the outer ends of the two opposing plungers 4 are hinged together.

[0043] When the main shaft 3 rotates, the cylinder block 2 rotates synchronously with the main shaft 3, and each plunger 4 on the cylinder block 2 revolves around the main shaft 3. Since the axes of the two cylinder blocks 2 are inclined relative to the main shaft 3 and are arranged in a V-shape symmetrically, the plungers 4 will reciprocate along the plunger holes 22 of the cylinder block 2 during the revolution, thereby completing the oil suction and discharge, allowing the plunger pump to continuously output pressurized oil.

[0044] like Figure 3 and Figure 4 As shown, the two opposing plungers 4 are hinged together by a pin 5. Each pin 5 is located on the symmetrical plane of the two cylinders 2, and the axis of each pin 5 is perpendicular to the plane where the axis of the corresponding two plungers 4 are located.

[0045] like Figure 3 , Figure 7 and Figure 8 As shown, in the aforementioned twin-cylinder tilting opposed V-type plunger pump, the plunger 4 has an axially extending hole 43 penetrating its inner end face, and the hole 43 is filled with low-density packing 6. The low-density packing 6 can effectively reduce the overall weight of the plunger 4. In actual manufacturing, the low-density packing 6 can be a lightweight alloy or engineering plastic.

[0046] like Figure 7 and Figure 8 As shown, in the two opposing plungers 4, one plunger 4 has two plate-shaped hinge protrusions 41 protruding axially from its outer end, and the other plunger 4 has a plate-shaped hinge protrusion 42 protruding axially from its middle outer end. The hinge protrusion 42 is embedded between the two hinge protrusions 41, and the pin 5 passes vertically through the two hinge protrusions 41 and the hinge protrusion 42.

[0047] like Figure 3As shown, two swashplates 7 are fixedly installed inside the housing 1, located on the outer sides of the two cylinders 2 respectively. The inner surface of each swashplate 7 is parallel and directly opposite the outer end face of the cylinder 2 on the same side. A distribution plate 8 is provided between each swashplate 7 and the cylinder 2 on the same side. The distribution plate 8 is fixedly connected to the swashplate 7 and fits against the outer end face of the cylinder 2. Figure 5 , Figure 10 and Figure 11 As shown, the swash plate 7 has four oil passage holes 81 arranged at intervals around the axis of the main shaft 3. Each plunger hole 22 penetrates the end face of the cylinder body 2 near the distribution plate 8. When the cylinder body 2 rotates with the main shaft 3, each plunger hole 22 will alternately connect with the oil passage hole 81, thereby cooperating with the extension and retraction of the plunger 4 to complete the oil suction and discharge.

[0048] like Figure 3 and Figure 5 As shown, the swash plate 7 has an inwardly extending annular flange 71 along its circumferential direction, and the outer circumferential surface of the cylinder body 2 abuts against the inner circumferential surface of the annular flange 71. The annular flange 71 can provide radial limiting and guiding for the cylinder body 2, limiting radial displacement during operation and ensuring stable rotation of the cylinder body 2.

[0049] like Figure 3 As shown, two annular protrusions 31 are formed on the outer wall of the main shaft 3, spaced apart along the axial direction. Each annular protrusion 31 is arranged circumferentially along the main shaft 3 and has a spherical surface. The two cylinders 2 are fitted onto the two annular protrusions 31 in a one-to-one correspondence. Further, as... Figure 3 , Figure 6 and Figure 9 As shown, the outer end of the mounting hole 21 is a stepped hole section 211 with an increased radial dimension. The stepped hole section 211 and the small diameter section of the mounting hole 21 are transitioned by an annular stepped surface 212. A retaining ring 9 is fixedly embedded on the inner circumferential wall of the stepped hole section 211. Each annular protrusion 31 of the main shaft 3 is fitted with a support ring 10 that abuts against the stepped surface 212, and the inner circumferential surface of the support ring 10 slides in contact with the annular protrusion 31. A corrugated gasket 11 with a circumferential wave shape is sandwiched between the retaining ring 9 and the adjacent support ring 10. In this structure, the corrugated gasket 11 pushes the support ring 10, so that the support ring 10 abuts against the stepped surface 212, thus positioning the support ring 10. At this time, since the inner circumferential surface of the support ring 10 slides in contact with the annular protrusion 31, the annular protrusion 31 forms a rigid fulcrum, so that the corrugated gasket 11 generates a reverse pushing force against the retaining ring 9, thereby pressing the cylinder body 2 onto the distribution plate 8.

[0050] like Figure 9 and Figure 12As shown, each annular protrusion 31 has several cylindrical protrusions 32 spaced circumferentially along the main shaft 3. Several circumferentially spaced grooves 23 are formed on the inner circumferential wall of the mounting hole 21 of the cylinder body 2. The grooves 23 are straight and parallel to the axis of the cylinder body 2, and the protrusions 32 are correspondingly embedded in the grooves 23. The protrusions 32 embedded in the grooves 23 enable circumferential positioning of the main shaft 3 and the cylinder body 2. The torque transmitted by the protrusions 32 drives the cylinder body 2 to rotate synchronously with the main shaft 3. Preferably, the diameter of the protrusions 32 matches the width of the grooves 23.

[0051] Example 2

[0052] This embodiment is basically the same as embodiment one in structure and principle, except that: Figure 13 and Figure 14 As shown, several plunger holes 22 are arranged in two concentric rings on the cylinder block 2, with an equal number of plunger holes 22 in both rings. The plunger holes 22 in each ring are evenly spaced along the circumference of the cylinder block 2. The plunger holes 22 in the inner ring and the plunger holes 22 in the outer ring are staggered radially along the cylinder block 2, so that the spacing between adjacent plunger holes 22 in the inner ring and the outer ring is radially opposite. During the operation of the plunger pump, when the oil discharge from the outer ring plunger holes 22 reaches a low point, it is precisely compensated by the oil discharge from the inner ring plunger holes 22, making the total output flow more stable, significantly reducing flow pulsation and pressure pulsation, and improving the operational stability of the plunger pump.

[0053] In actual manufacturing, the oil passage holes 81 on the oil distribution plate 8 can adopt a structure of inner and outer double-ring arc-shaped oil passage holes 81 according to the staggered arrangement and phase relationship of the inner and outer rings of plunger holes 22, so that both the inner and outer rings of plunger holes 22 can complete the oil suction and discharge work. How the medium of the plunger holes 22 achieves oil suction and discharge work through the oil passage holes 81 of the oil distribution plate 8 can be achieved using existing technology, which will not be described in detail here.

[0054] The specific embodiments described herein are merely illustrative of the spirit of the invention. Those skilled in the art to which this invention pertains may make various modifications or additions to the described specific embodiments or use similar methods to substitute them, without departing from the spirit of the invention or exceeding the scope defined by the appended claims.

[0055] Although this document frequently uses terms such as 1. housing; 2. cylinder block; 21. mounting hole; 211. stepped hole section; 212. stepped surface; 22. plunger hole; 23. groove; 3. spindle; 31. annular protrusion; 32. protruding post; 4. plunger; 41. hinged protrusion one; 42. hinged protrusion two; 43. recessed hole; 5. pin; 6. low-density packing; 7. swashplate; 71. annular flange; 8. distributor plate; 81. oil passage hole; 9. retaining ring; 10. support ring; 11. corrugated gasket, etc., the possibility of using other terms is not excluded. The use of these terms is merely for the convenience of describing and explaining the essence of the invention; interpreting them as any additional limitation would contradict the spirit of the invention.

Claims

1. A double-cylinder tilting V-type plunger pump, comprising a housing (1), two cylinders (2), and a main shaft (3) rotatably disposed within the housing (1), wherein each cylinder (2) is a disc-shaped component with an axially formed mounting hole (21) in the center, the two cylinders (2) are respectively fitted onto the main shaft (3) through their respective mounting holes (21) and rotate synchronously with the main shaft (3), the axes of the two cylinders (2) are tilted relative to the main shaft (3), and the two cylinders (2) are arranged symmetrically in a V-shape, wherein a plurality of plunger holes (22) are sequentially arranged circumferentially on the cylinders (2), characterized in that, The axial direction of the plunger hole (22) is parallel to the axial direction of the cylinder (2). A cylindrical plunger (4) coaxial with the plunger hole (22) is slidably arranged in each plunger hole (22). The outer end of each plunger (4) extends out of the plunger hole (22). The plungers (4) on the two cylinders (2) are arranged facing each other, and the outer ends of the two opposing plungers (4) are hinged together.

2. The dual-cylinder tilting opposed V-type piston pump according to claim 1, characterized in that, The two plungers (4) facing each other are hinged together by a pin (5). Each pin (5) is located on the symmetrical plane of the two cylinders (2), and the axis of each pin (5) is perpendicular to the plane where the axis of the corresponding two plungers (4) are located.

3. The dual-cylinder tilting opposed V-type piston pump according to claim 2, characterized in that, In the two opposing plungers (4), the outer end of one plunger (4) protrudes axially to form two plate-shaped hinge protrusions (41), and the middle part of the outer end of the other plunger (4) protrudes axially to form a plate-shaped hinge protrusion (42). The hinge protrusion (42) is embedded between the two hinge protrusions (41), and the pin (5) penetrates vertically through the two hinge protrusions (41) and the hinge protrusion (42).

4. The dual-cylinder tilting opposed V-type piston pump according to claim 1, 2, or 3, characterized in that, The plunger (4) has an axially extending hole (43) that penetrates its inner end face, and the hole (43) is filled with low-density filler (6).

5. The dual-cylinder tilting opposed V-type piston pump according to claim 1, 2, or 3, characterized in that, The housing (1) is fixedly provided with two swashplates (7) located on the outside of the two cylinders (2). The inner side of each swashplate (7) is parallel to and directly opposite the outer end face of the cylinder (2) on the same side. Each swashplate (7) is provided with a distribution plate (8) between it and the cylinder (2) on the same side. The distribution plate (8) is fixedly connected to the swashplate (7) and fits against the outer end face of the cylinder (2).

6. The dual-cylinder tilting opposed V-type piston pump according to claim 5, characterized in that, The swash plate (7) has an inwardly extending annular flange (71) along its circumferential direction, and the outer circumferential surface of the cylinder body (2) is in contact with the inner circumferential surface of the annular flange (71).

7. The dual-cylinder tilting opposed V-type piston pump according to claim 1, 2, or 3, characterized in that, Two annular protrusions (31) are formed on the outer wall of the main shaft (3) and are spaced apart along the axial direction. Each annular protrusion (31) is arranged circumferentially along the main shaft (3) and has a spherical surface. The two cylinders (2) are fitted on the two annular protrusions (31) in a one-to-one correspondence.

8. The dual-cylinder tilting opposed V-type piston pump according to claim 7, characterized in that, The outer end of the mounting hole (21) is a stepped hole section (211) with an increased radial dimension. The stepped hole section (211) and the small diameter section of the mounting hole (21) are connected by an annular stepped surface (212). A retaining ring (9) is fixedly embedded on the inner circumferential wall of the stepped hole section (211). Each annular protrusion (31) of the main shaft (3) is fitted with a support ring (10) that abuts against the stepped surface (212). The inner circumferential surface of the support ring (10) slides in contact with the annular protrusion (31). A corrugated gasket (11) with a wavy shape along the circumferential direction is sandwiched between the retaining ring (9) and the adjacent support ring (10).

9. The dual-cylinder tilting opposed V-type piston pump according to claim 7, characterized in that, Each annular protrusion (31) is provided with several cylindrical protrusions (32) spaced apart along the circumference of the main axis (3). Several grooves (23) spaced apart along the circumference are provided on the inner circumferential wall of the mounting hole (21) of the cylinder body (2). The grooves (23) are straight and parallel to the axis of the cylinder body (2). The protrusions (32) are embedded in the grooves (23) one by one.

10. The dual-cylinder tilting opposed V-type piston pump according to claim 1, characterized in that, Several plunger holes (22) are arranged in two rings on the cylinder body (2), with the number of plunger holes (22) in the inner and outer rings being equal. Each plunger hole (22) in each ring is evenly spaced along the circumference of the cylinder body (2). The plunger holes (22) in the inner ring and the plunger holes (22) in the outer ring are staggered along the radial direction of the cylinder body (2).

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