A non-through-shaft floating swash plate type axial piston pump of a main shaft constant speed driving rotary disc

Abstract

The application discloses a non-through-shaft floating swash plate type axial plunger pump of a rotary disc driven by a main shaft at a constant speed. When a central synchronous shaft rotates, rollers and a rolling track always keep linear contact; when a ball fork synchronous shaft operates, balls and a track always keep point contact. The central synchronous shaft and the ball fork synchronous shaft can compensate axial movement caused by working and installation errors between the rotary disc and the swash plate, and rely on a central spring to exert pre-tightening force on the rotary disc, so as to provide initial pre-tightening force and pre-sealing force for the rotary disc / swash plate surface friction pair. Due to the existence of the central synchronous shaft or the ball fork synchronous shaft, a traditional standard cylindrical plunger can be designed into a thin rod plunger. In the whole rotation period, the thin rod plunger side surface is in zero contact with the cylinder hole wall surface, and the thin rod plunger is in a state of a two-force rod, so that the lateral force of the plunger can be effectively reduced, and a series of problems, such as easy overturning of a cylinder body and too large PV value caused by the lateral force of the plunger pair, are overcome.

Description

Technical Field

[0001] This invention relates to the field of piston pump technology, and in particular to a non-through-shaft floating swashplate axial piston pump with a constant-speed spindle-driven rotary table. Background Technology

[0002] Compared to traditional mechanical transmission, hydraulic transmission offers advantages such as higher power density, easier control, and superior dynamic performance. It is widely used in modern industrial systems, particularly in construction machinery. In my country, construction machinery plays a crucial role, and to date, most of my country's construction machinery utilizes hydraulic transmission technology. The hydraulic pump, as one of the core components of a hydraulic system, is the power source and boasts advantages such as high transmission power, long lifespan, simple and convenient variable control, and small size.

[0003] With the application of electrification technology in hydraulic transmission, traditional hydraulic technology faces continuous challenges, driving new demands for hydraulic technology. Electric motors possess operating characteristics such as low noise, wide speed range, and low-speed stability, all of which exceed the normal characteristics of traditional internal combustion engines. This necessitates a re-examination of the design of existing axial piston pumps to better adapt to the development needs of electric drive technology in main equipment. Most hydraulic systems in my country's construction machinery use piston pumps as the power source for the entire hydraulic system; therefore, analyzing and studying the characteristics of axial piston pumps plays a crucial role in improving the performance of the entire hydraulic system.

[0004] Traditional fixed swashplate-type non-through-shaft axial piston pumps suffer from a series of problems, including excessive lateral force on the piston pair, leading to cylinder overturning (directly affecting the sealing, lubrication, and load-bearing performance of the distribution pair), excessively long piston / cylinder bore contact length resulting in insufficient lubrication, and excessively high PV value. These issues make them difficult to meet the demands of new technologies for electrification. Therefore, this invention designs a non-through-shaft floating swashplate axial piston pump with a constant-speed driven rotary disc on the main shaft. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of existing technologies and address the limitations of current hydraulic pump technology, particularly the challenge of large lateral forces on the piston pair in non-through-shaft axial piston pumps. An innovative solution is proposed. By introducing a central synchronous shaft and a ball-fork synchronous shaft, this invention achieves precise constant-velocity drive between the rotary table and the cylinder block. This key technological breakthrough not only significantly reduces the lateral forces generated by the piston pair during operation but also effectively reduces frictional power loss during rotary table movement. This constant-velocity drive mechanism ensures stable pump performance under various operating conditions, improving pump efficiency and reliability. Simultaneously, the reduced lateral forces decrease pump wear, extend service life, and lower maintenance costs.

[0006] This invention is achieved through the following technical solution: A non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc includes a main shaft, a pump housing, and a pump body and a variable displacement housing mounted at both ends of the pump housing. The rear end of the main shaft passes through the pump body and extends into the pump housing. A cylinder block is connected to the rear end of the main shaft via a spline. A distribution plate is provided at the front end of the cylinder block. A rotary disc and a swashplate are sequentially arranged at the rear end of the cylinder block. Several cylinder holes are opened on the rear end face of the cylinder block. Ball sockets corresponding to the cylinder holes are opened on the front end face of the rotary disc. A thin rod plunger is connected between the corresponding cylinder holes and the ball sockets. A preload device mounting groove is opened at the center of the rear end face of the cylinder block, and a preload device is installed in the preload device mounting groove. A central synchronous shaft is provided between the cylinder block and the rotary disc. Push rod grooves are provided on both end faces of the central synchronous shaft. Three pivots are fixed at both ends of the central synchronous shaft. Each pivot has... The cylinder body and rotary table are equipped with spherical rollers. Corresponding circular groove raceways are provided on two opposite surfaces of the cylinder body and rotary table. The spherical rollers at both ends of the central synchronous shaft are located within the circular groove raceways of the cylinder body and rotary table, respectively. Push rod grooves are provided at the center of the rotary table and at one end of the preload device. Push rods are provided between the push rod grooves at both ends of the central synchronous shaft and between the push rod groove at the center of the rotary table and the push rod groove at one end of the preload device. The rear end face of the rotary table is in close contact with the front end face of the swashplate. The swashplate is mounted on the variable housing, and a variable mechanism is installed inside the variable housing. The rear end of the swashplate is connected to the variable mechanism. Multiple oil passages communicating with cylinder bores are opened on the front end face of the cylinder body. A distribution hole is opened on the distribution plate, communicating with the oil passages. An inlet / outlet oil port is opened on the pump body, communicating with the distribution hole.

[0007] The pre-tightening device includes a cylinder placed in a pre-tightening device mounting groove, a spring placement groove at the front end of the cylinder, a spring placed in the spring placement groove, and the two ends of the spring pressing the cylinder and the cylinder body respectively. The rear end of the cylinder is provided with the push rod groove.

[0008] A central groove is formed at the center of the rear end face of the rotary table, and a protrusion is formed at the center of the front end face of the swashplate. The rotary table is closely attached to the swashplate, and the protrusion is located within the central groove. Multiple grooves corresponding to the ball sockets are formed on the rear end face of the rotary table, and multiple oil guide channels corresponding to the grooves are formed inside the rotary table. The two ends of the oil guide channels are connected to the grooves and the ball sockets, respectively.

[0009] A shim is provided between the rotary table and the swash plate.

[0010] A non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disk includes a main shaft, a pump housing, and a pump body and a variable displacement housing mounted at both ends of the pump housing. The rear end of the main shaft passes through the pump body and extends into the pump housing. A cylinder block is connected to the rear end of the main shaft via a spline. A distribution plate is provided at the front end of the cylinder block. A rotary disk and a swashplate are sequentially provided at the rear end of the cylinder block. A plurality of cylinder holes are opened on the rear end face of the cylinder block. Ball sockets corresponding to the cylinder holes are opened on the front end face of the rotary disk. A thin rod plunger connects the ball and socket. A ball fork groove is opened at the center of the rear end face of cylinder two. A ball fork synchronous shaft is provided between cylinder two and rotary table two. The front end of the ball fork synchronous shaft extends into the ball fork groove and is connected to cylinder two via a spline. A spring placement groove is opened on the front end face of the ball fork synchronous shaft, and a spring is placed in the spring placement groove. The two ends of the spring respectively press against cylinder two and ball fork synchronous shaft. The rear end of the ball fork synchronous shaft extends out of the ball fork groove. Ball fork positioning ball grooves are provided at the center of the rear end face of the ball fork synchronous shaft and the center of the front end face of rotary table two. Four symmetrical curved grooves are provided on the outside of each ball fork positioning ball groove. A ball fork positioning ball is provided between the ball fork positioning ball groove on the rear end face of the ball fork synchronous shaft and the ball fork positioning ball groove on the front end face of rotary table two. The four curved grooves on the rear end face of the ball fork synchronous shaft are offset from the four curved grooves on the front end face of rotary table two by a certain angle, so that the four curved grooves on the rear end face of the ball fork synchronous shaft and the four curved grooves on the front end face of rotary table two are offset from each other by a certain angle. Four ball-and-fork steel ball tracks are constructed, and the four ball-and-fork steel balls are placed in the four ball-and-fork steel ball tracks respectively; the rear end face of the rotary table two is closely attached to the front end face of the swashplate, the swashplate is mounted on the variable housing, and a variable mechanism is installed inside the variable housing, the rear end of the swashplate is connected to the variable mechanism; multiple oil passages communicating with cylinder bores are opened on the front end face of the cylinder block two, a distribution hole is opened on the distribution plate, the distribution hole is connected to the oil passages, and an oil inlet and outlet port is opened on the pump body, the oil inlet and outlet port is connected to the distribution hole.

[0011] A central groove is formed at the center of the rear end face of the rotary table two, and a protrusion is formed at the center of the front end face of the swashplate. The rotary table two is in close contact with the swashplate, and the protrusion is located within the central groove. Multiple grooves corresponding to the ball sockets are formed on the rear end face of the rotary table two, and multiple oil guide channels corresponding to the grooves are formed inside the rotary table two. The two ends of the oil guide channels are connected to the grooves and the ball sockets, respectively.

[0012] A shim is provided between the rotary table 2 and the swash plate.

[0013] The variable mechanism includes a variable piston located inside a variable housing. An adjusting screw is connected to one end of the variable piston. An adjusting handwheel connected to the adjusting screw is provided on the side of the variable housing. A spherical protrusion is provided at the center of the rear end face of the swashplate. A circular groove matching the spherical protrusion is opened on the side of the variable piston. The spherical protrusion is located in the circular groove. By adjusting the handwheel and the adjusting screw, the variable piston is driven to slide inside the variable housing, thereby adjusting the tilt angle of the swashplate.

[0014] The advantages of this invention are: 1. The constant-speed rotation component of this invention achieves constant-speed rotation between the rotary disc and the cylinder in a non-through-shaft floating swashplate axial piston pump through the design of the central synchronous shaft and the ball fork synchronous shaft. This design not only ensures line contact between the rollers and raceways when the central synchronous shaft is running, but also guarantees point contact between the balls and raceways when the ball fork synchronous shaft is running, thereby significantly improving the stability and reliability of torque transmission.

[0015] 2. The design of the central synchronous shaft and ball fork synchronous shaft of this invention not only provides compensation for axial movement, but also achieves preload control of the rotary table through the central spring. This design allows the system to automatically adjust the preload in the face of changes in workload and installation errors, ensuring that the friction pair between the rotary table and the swashplate always maintains the optimal preload condition.

[0016] 3. Compared with traditional non-through-shaft axial piston pumps, this invention ensures precise synchronous movement of the cylinder block and rotary table through the design of a central synchronous shaft and a ball fork synchronous shaft. The traditional standard cylindrical piston can therefore be designed as a thin rod piston. Throughout the entire rotation cycle, the side of the thin rod piston has zero contact with the cylinder bore wall. The thin rod piston is in a "two-force rod" state, which can effectively reduce the lateral force of the piston and overcome a series of problems caused by the lateral force of the piston pair, such as easy cylinder overturning (directly affecting the sealing and lubrication bearing performance of the distribution pair) and excessive PV value. At the same time, since only the tail of the thin rod piston contacts the cylinder bore wall, the piston / cylinder bore contact length is also significantly reduced, ensuring the lubrication performance of the piston pair under all operating conditions throughout the entire operating cycle. Attached Figure Description

[0017] Figure 1 This is a cross-sectional view of the middle part of a non-through-shaft floating swashplate axial piston pump with constant speed drive of the spindle according to the present invention. Figure 1 a is the central synchronous axis Figure 1 b is the synchronous shaft of the ball fork). Figure 2 This is a partial sectional view of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc of the main shaft according to the present invention. Figure 2 a is the central synchronous axis Figure 2 b is the synchronous shaft of the ball fork). Figure 3This is a schematic diagram of the rotary disk structure of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disk of the main shaft according to the present invention. Figure 3 a is a front view of a rotary table. Figure 3 b is a half-section view of the rotary table. Figure 3 c is a rear view of the rotary table); Figure 4 This is a schematic diagram of the cylinder block structure of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc of the main shaft according to the present invention. Figure 4 a is a front view of the cylinder block. Figure 4 (b is a half-section view of the cylinder block) Figure 5 This is a schematic diagram of the rotary disk, cylinder block, central synchronous shaft, and roller structure of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disk of the main shaft according to the present invention. Figure 5 Figure a shows the assembly diagram of the rotary table, central synchronous shaft, and rollers. Figure 5 (b is a schematic diagram of the assembly of cylinder block 1, central synchronous shaft, and rollers). Figure 6 This is a schematic diagram of the rotary disk, ball fork, and center ball structure of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disk of the main shaft according to the present invention. Figure 6 a represents rotary table two. Figure 6 b is a ball fork); Figure 7 This is a schematic diagram of the rotary disk, ball fork, and center ball structure of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disk of the main shaft according to the present invention. Figure 7 a represents the second rotary table and the center ball bearing. Figure 7 b represents the ball fork and the central ball). Figure 8 This is a schematic diagram of the cylinder block structure of a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc of the main shaft according to the present invention. Figure 8 a is a two-sided front view of the cylinder block. Figure 8 (b is a cross-sectional view of the cylinder block in two halves); Figure 9 This is a schematic diagram of the distribution plate structure of a non-through-shaft floating swashplate axial piston pump with a constant speed drive rotary disc of the main shaft according to the present invention.

[0018] Numbering on the map: Main shaft 1, variable housing 2, pump body 3, distributor plate 4, pump housing 5, variable piston 6.1, adjusting screw 6.2, adjusting handwheel 6.3, spherical protrusion 6.4, dial 6.5, swashplate 7, rotary table one 8.1, rotary table two 8.2, thin rod plunger 9, push rod 10, preload device mounting slot 11, cylinder 11.1, cylinder one 12.1, cylinder two 12.2, central synchronous shaft 13, pivot Shaft 13.1, spherical roller 13.2, ball fork synchronous shaft 14, ball fork positioning ball 15.1, ball fork steel ball 15.2, ball fork positioning ball groove 15.3, curved groove 15.4, circular groove raceway 16, push rod groove 17, ball socket 18, spring 19, oil passage 20, ball fork groove 21, distribution hole 22, oil inlet / outlet port 23, cylinder bore 24, groove 25, oil guide channel 26, gasket 27. Detailed Implementation Example 1:

[0019] like Figure 1-5As shown in Figure 9, a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc includes a main shaft 1, a pump housing 5, and a pump body 3 and a variable displacement housing 2 installed at both ends of the pump housing 5. The rear end of the main shaft 1 passes through the pump body 3 and extends into the pump housing 5. The rear end of the main shaft 1 is connected to a cylinder block 12.1 via a spline. A distribution plate 4 is provided at the front end of the cylinder block 12.1. A rotary disc 8.1 and a swashplate 7 are sequentially provided at the rear end of the cylinder block 12.1. A plurality of cylinder holes 24 are opened on the rear end face of the cylinder block 12.1. The cylinder body 12.1 has ball sockets 18 corresponding to the cylinder bores 24 one-to-one. A thin rod plunger 9 connects the corresponding cylinder bores 24 and ball sockets 18. A preload device mounting groove 11 is located at the center of the rear end face of the cylinder body 12.1, and a preload device is installed in the preload device mounting groove 11. A central synchronous shaft 13 is provided between the cylinder body 12.1 and the rotary table 8.1. Push rod grooves 17 are provided on the two end faces of the central synchronous shaft 13. Three pivots 13.1 are fixed at both ends of the central synchronous shaft 13. Each pivot 13.1 has... Spherical rollers 13.2 are installed. Circular groove raceways 16 corresponding to the spherical rollers 13.2 are provided on two opposite surfaces of the cylinder body 12.1 and the rotary table 8.1. The spherical rollers 13.2 at both ends of the central synchronous shaft 13 are located within the circular groove raceways 16 of the cylinder body 12.1 and the rotary table 8.1, respectively. Push rod grooves 17 are provided at the center of the rotary table 8.1 and at one end of the preload device. The push rod grooves 17 at both ends of the central synchronous shaft 13 correspond to the push rod groove 17 at the center of the rotary table 8.1 and the preload device... A push rod 10 is provided between the push rod grooves 17 at one end of the device. The rear end face of the rotary table 8.1 is close to the front end face of the swashplate 7. The swashplate 7 is mounted on the variable housing 2. A variable mechanism is installed inside the variable housing 2. The rear end of the swashplate 7 is connected to the variable mechanism. Multiple oil passages 20 communicating with the cylinder bore 24 are opened on the front end face of the cylinder block 12.1. A distribution hole 22 is opened on the distribution plate 4. The distribution hole 22 is communicating with the oil passages 20. An oil inlet and outlet port 23 is opened on the pump body 3. The oil inlet and outlet port 23 is communicating with the distribution hole 22.

[0020] The pre-tightening device includes a cylinder 11.1 placed in the pre-tightening device mounting groove 11. A spring placement groove is opened at the front end of the cylinder 11.1, and a spring 19 is placed in the spring placement groove. The two ends of the spring 19 respectively press the cylinder 11.1 and the cylinder 12.1. The push rod groove 17 is provided at the rear end of the cylinder 11.1.

[0021] A central groove is formed at the center of the rear end face of the rotary table 8.1, and a protrusion is formed at the center of the front end face of the swashplate 7. The rotary table 8.1 is in close contact with the swashplate 7, and the protrusion is located within the central groove. Multiple grooves 25, each corresponding to a ball socket 18, are provided on the rear end face of the rotary table 8.1. Multiple oil guide channels 26, each corresponding to a groove 25, are provided inside the rotary table 8.1. The two ends of each oil guide channel 26 communicate with the groove 25 and the ball socket 18, respectively.

[0022] A shim 27 is provided between the rotary table and the swash plate.

[0023] The main shaft 1 is connected to the cylinder 12.1 via a spline for rotation. The thin rod plunger 9 is clearance-fitted with the cylinder 12.1. The preload device is also clearance-fitted with the cylinder 12.1. A spring placement groove in the middle holds the spring 19 to provide preload force. One end of the push rod 10 at one end of the cylinder 12.1 is placed in the push rod groove 17 of the preload device, and the other end is placed in the push rod groove 17 of the central synchronous shaft 13, providing axial support. A spherical roller 13.2 mounted on one end of the central synchronous shaft 13 is placed in the cylinder 12.1. In the three circular groove raceways 16, the spherical roller 13.2 at the other end is placed in the three circular groove raceways 16 of the rotary table 8.1. The push rod 10 at one end of the rotary table 8.1 is placed in the push rod groove 17 of the rotary table 8.1 at one end and in another push rod groove 17 of the central synchronous shaft 13 at the other end. It is used to transmit the preload force of the preload device so that the rotary table 8.1 presses against the swashplate 7. The central groove of the rear end face of the rotary table 8.1 is placed on the protrusion of the swashplate 7 so that it can only rotate and move axially.

[0024] The main shaft 1 is connected to the cylinder 12.1 via a spline, driving the cylinder 12.1 to transmit torque to the spherical roller 13.2 of the central synchronous shaft 13 for synchronous rotation. Under the action of the push rod 10 and the cylinder 12.1, the spherical roller 13.2 transmits torque to the central synchronous shaft 13. The spherical roller 13.2 is embedded in the circular groove raceway 16 of the rotary table 8.1. The center of the spherical roller 13.2 always falls on the center line of the circular groove raceway 16. Therefore, the spherical surface of the spherical roller 13.2, driven by the three pivots, will contact the circular groove raceway 16 of the rotary table 8.1 and transmit torque, thereby driving the rotary table 8.1 to rotate. The spherical roller 13.2 allows its pivot axis to intersect with the corresponding circular groove raceway 16 on cylinder 12.1 and rotary disk 8.1. When the angle between the main shaft 1 and the central axis of rotary disk 8.1 is 0°, the automatic centering action of the central synchronous shaft 13 automatically aligns the axes of cylinder 12.1, central synchronous shaft 13, and rotary disk 8.1, resulting in uniform speed transmission. When the angle between the main shaft 1 and the central axis of rotary disk 8.1 is not 0°, the spherical roller 13.2 can move simultaneously along the pivot axis because the central synchronous shaft 13 changes angle under the action of the push rod 10. It can also slide along the corresponding circular groove raceway 16, so that the spherical surface of the spherical roller 13.2 is in contact with the corresponding circular groove raceway 16 surfaces of the cylinder 12.1 and the rotary table 8.1 respectively. The contact generatrix formed between the cylinder 12.1 and the central synchronous shaft 13 and the rotary table 8.1 and the central synchronous shaft 13 can ensure that the force transmission point of the spherical roller 13.2 is always located on the bisecting plane of the angle between the two axes of the main shaft 1 and the central shaft of the rotary table 8.1, and also has the characteristic of constant speed transmission. This ensures that the main shaft 1 and the rotary table 8.1 can always transmit power and always have constant speed transmission. Example 2:

[0025] like Figure 1-2As shown in Figures 6-9, a non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc includes a main shaft 1, a pump housing 5, and a pump body 3 and a variable displacement housing 2 installed at both ends of the pump housing 5. The rear end of the main shaft 1 passes through the pump body 3 and extends into the pump housing 5. The rear end of the main shaft 1 is connected to a cylinder block 12.2 via a spline. A distribution plate 4 is provided at the front end of the cylinder block 12.2. A rotary disc 8.2 and a swashplate 7 are sequentially provided at the rear end of the cylinder block 12.2. A plurality of cylinder holes 24 are opened on the rear end face of the cylinder block 12.2. A ball socket 18 corresponding to each cylinder hole 24 is opened on the front end face of the rotary disc 8.2. A thin rod plunger 9 is connected between the cylinder bore 24 and the ball socket 18. A ball fork groove 21 is opened at the center of the rear end face of the cylinder body 22.2. A ball fork synchronous shaft 14 is provided between the cylinder body 22.2 and the rotary table 28.2. The front end of the ball fork synchronous shaft 14 extends into the ball fork groove 21 and is connected to the cylinder body 22.2 through a spline. A spring placement groove is opened on the front end face of the ball fork synchronous shaft 14. A spring 19 is placed in the spring placement groove. The two ends of the spring 19 are respectively pressed against the cylinder body 22.2 and the ball fork synchronous shaft 14. The rear end of the ball fork synchronous shaft 14 extends out of the ball fork groove 21. At the center of the rear end face of the ball fork synchronous shaft 14... Both the center position of the front end face of rotary table 2 (8.2) and the center position of the ball fork positioning groove 15.3 are provided. Four symmetrical curved grooves 15.4 are provided on the outer side of each ball fork positioning groove 15.3. A ball fork positioning ball 15.1 is provided between the ball fork positioning groove 15.3 on the rear end face of the ball fork synchronous shaft 14 and the ball fork positioning groove on the front end face of rotary table 2 (8.2). The four curved grooves 15.4 on the rear end face of the ball fork synchronous shaft 14 are offset from the four curved grooves on the front end face of rotary table 2 (8.2) by a certain angle, so that the four curved grooves on the rear end face of the ball fork synchronous shaft 14 are aligned with the front end face of rotary table 2 (8.2). Four curved grooves form four ball-and-fork steel ball tracks, and four ball-and-fork steel balls 15.2 are placed in the four ball-and-fork steel ball tracks respectively; the rear end face of the rotary table 8.2 is close to the front end face of the swashplate 7, which is mounted on the variable housing 2. A variable mechanism is installed inside the variable housing 2, and the rear end of the swashplate 7 is connected to the variable mechanism; multiple oil passages 20 communicating with cylinder bores 24 are opened on the front end face of the cylinder block 12.2, and a distribution hole 22 is opened on the distribution plate 4, which communicates with the oil passages 20; an oil inlet / outlet port 23 is opened on the pump body 3, which communicates with the distribution hole 22.

[0026] A central groove is formed at the center of the rear end face of the rotary disk 8.2, and a protrusion is formed at the center of the front end face of the swashplate 7. The rotary disk 8.2 is in close contact with the swashplate 7, and the protrusion is located within the central groove. Multiple grooves 25, each corresponding to a ball socket 18, are provided on the rear end face of the rotary disk 8.2. Multiple oil guide channels 26, each corresponding to a groove 25, are provided inside the rotary disk 8.2. The two ends of each oil guide channel 26 communicate with the groove 25 and the ball socket 18, respectively.

[0027] A shim 27 is provided between the rotary table 2 and the swash plate.

[0028] The variable mechanism includes a variable piston 6.1 located within the variable housing 2. An adjusting screw 6.2 is connected to one end of the variable piston 6.1. An adjusting handwheel 6.3, connected to the adjusting screw 6.2, is located on the side of the variable housing 2. A spherical protrusion 6.4 is located at the center of the rear end face of the swashplate 7. A circular groove matching the spherical protrusion 6.4 is formed on the side of the variable piston 6.1, with the spherical protrusion 6.4 located within the circular groove. By adjusting the handwheel 6.3 and the adjusting screw 6.2, the variable piston 6.1 slides within the variable housing 2, adjusting the tilt angle of the swashplate 7. Changing the flow rate within the variable housing 2 is achieved by external force rotating the adjusting handwheel 6.3 and the adjusting screw 6.2, causing the variable piston 6.1 to move axially and simultaneously causing the swashplate 7 to rotate around its center, thus changing the tilt angle of the swashplate 7 and achieving the variable flow purpose. When the desired flow rate is reached, it can be tightened by locking the nut. Turning the adjusting handwheel 6.3 clockwise decreases the flow rate. Turning the adjusting handwheel 6.3 counterclockwise increases the flow rate. Its percentage value can be roughly read from the 6.5 mark on the dial. When changing the flow rate during operation, unloading is required. If installed on top of the oil tank, a small deflection angle during starting is not conducive to the oil pump's self-priming; the deflection angle should be increased before starting.

[0029] The ball fork synchronous shaft 14 is splined to the cylinder 12.2 and can rotate synchronously. One end of the ball fork synchronous shaft 14 is provided with a spring placement groove for placing the spring and giving the ball fork synchronous shaft 14 a preload. The ball fork synchronous shaft 14 transmits the preload to the rotary table 8.2 through the central positioning ball, so that it presses against the swashplate 7.

[0030] The ball-fork synchronous shaft 14 and the rotary table 8.2 each have four symmetrical curved grooves 15.4 in their ball-fork positioning ball grooves. After assembly, these form two intersecting annular grooves centered on the ball-fork positioning ball 15.1, serving as a ball-fork steel ball track. The four ball-fork steel balls 15.2 are placed in the ball-fork steel ball track and can move along it. When the swashplate 7 tilts, the ball-fork steel balls 15.2 transmit the force of the ball-fork synchronous shaft 14 to the rotary table 8.2. Since the curved grooves on the ball-fork synchronous shaft 14 and the rotary table 8.2 are symmetrically arranged and located on two intersecting planes (in this embodiment, these are perpendicular planes), the centers of the ball-fork steel balls 15.2 are all located at the intersection of the spherical surfaces, resulting in equal angular velocities. This ensures that power can always be transmitted between the main shaft 1 and the rotary table 8.2, and that the transmission is always at a constant speed.

Claims

1. A non-through-shaft floating swashplate axial piston pump with a constant-speed spindle-driven rotary table, characterized in that: The system includes a main shaft, a pump housing, and pump body and variable displacement housing mounted at both ends of the pump housing. The rear end of the main shaft passes through the pump body and extends into the pump housing. A cylinder block is connected to the rear end of the main shaft via a spline. A distribution plate is located at the front end of the cylinder block, and a rotary disk and a swashplate are sequentially located at the rear end of the cylinder block. Several cylinder holes are formed on the rear end face of the cylinder block, and ball sockets corresponding to the cylinder holes are formed on the front end face of the rotary disk. Thin rod plungers are connected between the corresponding cylinder holes and ball sockets. A preload device mounting groove is located at the center of the rear end face of the cylinder block, and a preload device is installed in the preload device mounting groove. A central synchronous shaft is located between the cylinder block and the rotary disk. Push rod grooves are provided on both end faces of the central synchronous shaft. Three pivots are fixed at both ends of the central synchronous shaft, and spherical rollers are mounted on each pivot. Both opposite surfaces of the rotary table one are provided with circular groove raceways corresponding to the spherical rollers. The spherical rollers at both ends of the central synchronous shaft are located in the circular groove raceways of the cylinder body one and the rotary table one, respectively. A push rod groove is provided at the center of the rotary table one and at one end of the preload device. A push rod is provided between the push rod grooves at both ends of the central synchronous shaft and the push rod grooves at the center of the rotary table one and at one end of the preload device. The rear end face of the rotary table one is in close contact with the front end face of the swashplate. The swashplate is mounted on the variable housing, and a variable mechanism is installed inside the variable housing. The rear end of the swashplate is connected to the variable mechanism. Multiple oil passages communicating with the cylinder bores are opened on the front end face of the cylinder body one. A distribution hole is opened on the distribution plate, and the distribution hole communicates with the oil passages. An oil inlet and outlet port is opened on the pump body, and the oil inlet and outlet port communicates with the distribution hole. The pre-tightening device includes a cylinder placed in a pre-tightening device mounting groove, a spring placement groove at the front end of the cylinder, a spring placed in the spring placement groove, the two ends of the spring pressing the cylinder and the cylinder body respectively, and the top rod groove is provided at the rear end of the cylinder. A central groove is provided at the center of the rear end face of the rotary disk one, and a protrusion is provided at the center of the front end face of the swashplate. The rotary disk one is closely attached to the swashplate, and the protrusion is located in the central groove.

2. The non-through-shaft floating swashplate axial piston pump with constant velocity drive of the spindle as described in claim 1, characterized in that: The rear end face of the rotary table is provided with a plurality of grooves corresponding to the ball sockets, and the interior of the rotary table is provided with a plurality of oil guide channels corresponding to the grooves, with the two ends of the oil guide channels communicating with the grooves and the ball sockets respectively.

3. A non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc as described in claim 1, characterized in that: A shim is provided between the rotary table and the swash plate.

4. A non-through-shaft floating swashplate axial piston pump with a constant-speed spindle-driven rotary table, characterized in that: The system includes a main shaft, a pump housing, and a pump body and a variable displacement housing mounted at both ends of the pump housing. The rear end of the main shaft passes through the pump body and extends into the pump housing. A second cylinder is connected to the rear end of the main shaft via a spline. A distribution plate is located at the front end of the second cylinder, and a second rotary disk and a swashplate are sequentially located at the rear end of the second cylinder. Several cylinder holes are formed on the rear end face of the second cylinder, and ball sockets corresponding to the cylinder holes are formed on the front end face of the second rotary disk. A thin rod plunger connects the corresponding cylinder hole and ball socket. A ball fork groove is formed at the center of the rear end face of the second cylinder. A ball fork synchronous shaft is located between the second cylinder and the second rotary disk. The front end of the ball fork synchronous shaft extends into the ball fork groove and is connected to the second cylinder via a spline. A spring placement groove is formed on the front end face of the ball fork synchronous shaft, and a spring is placed in the spring placement groove. The two ends of the spring respectively press against the second cylinder and the ball fork synchronous shaft. The rear end of the ball fork synchronous shaft extends out of the ball fork groove. Ball fork anchors are located at the center of the rear end face of the ball fork synchronous shaft and the center of the front end face of the second rotary disk. The ball positioning groove has four symmetrical curved grooves on the outside of each ball positioning groove. A ball positioning ball is provided between the ball positioning groove on the rear end face of the ball fork synchronous shaft and the ball positioning groove on the front end face of the rotary table two. The four curved grooves on the rear end face of the ball fork synchronous shaft and the four curved grooves on the front end face of the rotary table two are offset at a certain angle, so that the four curved grooves on the rear end face of the ball fork synchronous shaft and the four curved grooves on the front end face of the rotary table two form four ball fork steel ball tracks. The four ball fork steel balls are placed in the four ball fork steel ball tracks respectively. The rear end face of the rotary table two is close to the front end face of the swashplate. The swashplate is mounted on the variable housing. A variable mechanism is installed in the variable housing. The rear end of the swashplate is connected to the variable mechanism. Multiple oil passages communicating with the cylinder bore are opened on the front end face of the cylinder body two. A distribution hole is opened on the distribution plate, and the distribution hole communicates with the oil passages. An oil inlet and outlet port is opened on the pump body, and the oil inlet and outlet port communicates with the distribution hole. A central groove is provided at the center of the rear end face of the rotary disk II, and a protrusion is provided at the center of the front end face of the inclined plate. The rotary disk II is closely attached to the inclined plate, and the protrusion is located in the central groove.

5. A non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc as described in claim 4, characterized in that: The rear end face of the rotary table two is provided with a plurality of grooves corresponding to the ball sockets, and the interior of the rotary table two is provided with a plurality of oil guide channels corresponding to the grooves, with the two ends of the oil guide channels communicating with the grooves and the ball sockets respectively.

6. A non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc as described in claim 4, characterized in that: A shim is provided between the rotary table 2 and the swash plate.

7. A non-through-shaft floating swashplate axial piston pump with a constant velocity drive rotary disc as described in claim 1 or 4, characterized in that: The variable mechanism includes a variable piston located inside a variable housing. An adjusting screw is connected to one end of the variable piston. An adjusting handwheel connected to the adjusting screw is provided on the side of the variable housing. A spherical protrusion is provided at the center of the rear end face of the swashplate. A circular groove matching the spherical protrusion is opened on the side of the variable piston. The spherical protrusion is located in the circular groove. By adjusting the handwheel and the adjusting screw, the variable piston is driven to slide inside the variable housing, thereby adjusting the tilt angle of the swashplate.

Images