CN221347141U - Floating swash plate type axial plunger pump with symmetrical inclined rotating assemblies - Google Patents

Abstract

The utility model discloses a floating inclined plate type axial piston pump with a symmetrical inclined rotating component, a turntable is arranged on the main shaft of the inner cavity of the pump body, the same number of ball sockets are symmetrically arranged on the two sides of the turntable, ball joints are splined or integrally formed on the main shaft on both sides of the turntable, cylinder bodies are sleeved on the ball joints, a plurality of cylinder holes are arranged on the side of the cylinder body close to the turntable, the cylinder holes correspond to the ball sockets one by one, thin rod plungers are arranged in the cylinder holes, the end plunger balls of the thin rod plungers extend out of the cylinder holes and extend into the corresponding ball sockets, a distribution plate is arranged on the side of the two cylinder bodies away from the turntable, the distribution plate is tilted and fixed on the inner wall of the pump body, and the distribution plate seal is tightly attached to the cylinder body. The utility model realizes the reduction of flow pulsation, pressure pulsation and vibration noise of the plunger pump by greatly increasing the number of plungers, and basically eliminates the lateral force and friction of the plunger pair by designing a transmission mechanism that ensures the inclined cylinder body and the main shaft to rotate synchronously at the same speed.

Description

A floating swash plate axial piston pump with a symmetrically inclined rotating assembly

Technical Field

The utility model relates to the technical field of plunger pumps, in particular to a floating swash plate type axial plunger pump with a symmetrically inclined rotating component.

Background technique

The "dual carbon goal" is the main theme of the development of the world today, providing new opportunities and challenges for the application, innovation and development of fluid power technology. As an important supporting technology in equipment such as engineering machinery, aerospace and navigation, and manufacturing, fluid power needs to accelerate its evolution in the energy transition to provide support for the upgrading of electromechanical equipment. The prime mover of construction machinery is replaced by an electric motor from an internal combustion engine. Due to the completely different technical characteristics of electric motors and internal combustion engines, the electrification of construction machinery has put forward new technical requirements and demands for the hydraulic power component of the swash plate axial piston pump. The plunger and slipper assembly in the traditional plunger and slipper type swash plate axial piston pump and its related plunger pair and slipper pair are the key to the traditional plunger and slipper type swash plate axial piston pump being unable to adapt to the new technical requirements and demands of electrification. Due to the excessive lateral force of the plunger pair, the cylinder body is easy to overturn (directly affecting the sealing and lubrication bearing performance of the distribution pair), the plunger/cylinder hole contact length is too long, the lubrication is insufficient, the PV value is too large, and the variable inclination angle of the swash plate is generally limited to no more than 20°. The excessive centrifugal force of the slipper in the slipper pair causes the slipper to overturn and wear eccentrically, and the plunger cavity oil suction negative pressure is insufficient, resulting in serious air cavitation.

In this context, the utility modeler proposed a new type of floating swash plate axial piston pump, which transfers the huge lateral force of the plunger pair based on the "two-force rod" principle, offsets the huge lateral force of the plunger pair based on the principle of static pressure support, and designs floating swash plate axial piston pumps with various structural schemes accordingly, and applies for a series of national utility model patents. The existing traditional axial piston pumps, floating cup pumps and previously designed floating swash plate axial piston pumps still have technical deficiencies, mainly manifested in that the number of plungers in the existing traditional axial piston pumps and previously designed floating swash plate axial piston pumps is generally 9 to 11, and the number of plungers is small, resulting in large flow pulsation, large pressure pulsation, and significant pump vibration and noise. The floating cup pump is a new type of axial piston pump developed by INNAS in the Netherlands in recent years, which has achieved the expansion of the number of pump plungers to 24, significantly reducing the flow pulsation, pressure pulsation and vibration noise of the pump, but also brings new problems. The plunger of the float cup pump is a fixed plunger, that is, it is fixed on the main shaft, and the plunger and the main shaft have no relative motion freedom. The cylinder body is a split cylinder body, and the plunger cavity is independently designed into a new part called "cup body". The cup body is movably mounted on the fixed plunger, and at the same time, the two ends of the cup body are clamped in the split cylinder body. The cup body has a certain space of relative sliding motion freedom relative to the split cylinder body, which is the origin of the name of the "float cup pump". The cup body of the float cup pump is driven by the plunger and the split cylinder body clamped on both sides of the cup body, and the split cylinder body of the float cup pump The split cylinder body and the cup body are connected to and transmit torque to the main shaft through a transmission pin. Since the split cylinder body and the cup body are arranged at an angle compared to the main shaft, the rotation axis of the split cylinder body of the float cup pump and the rotation axis of the main shaft are not on the same axis, but at an axis angle. Therefore, the rotation speed of the split cylinder body of the float cup pump and the rotation speed of the main shaft are not completely equal. Therefore, the plunger pair of the float cup pump still has intermittent periodic lateral force and friction. There is also a certain degree of relative sliding motion between the floating cup body of the float cup pump and the split cylinder body that clamps the cup body, which will also generate friction.

Utility Model Content

The purpose of the utility model is to make up for the defects of the existing technology, further improve the floating swash plate type axial piston pump technical system of the utility model, and propose a floating swash plate type axial piston pump with a symmetrical inclined rotating component.

The utility model is realized by the following technical solutions:

A floating inclined plate axial piston pump with a symmetrically inclined rotating component includes a pump body, a main shaft is installed in the pump body, a turntable is installed on the main shaft, the same number of ball sockets are symmetrically arranged on two sides of the turntable, and ball joints are spline-connected or integrally formed on the main shaft at both sides of the turntable, a cylinder body is installed on the outside of each ball joint, and a plurality of cylinder holes are arranged on a surface of each cylinder body close to the turntable, and the cylinder holes correspond to the ball sockets one by one, and a thin rod plunger is arranged in each cylinder hole, and the end plunger ball head of the thin rod plunger extends out of the cylinder hole and extends into the ball socket of the turntable corresponding to it, and a distribution plate is arranged on the side of the two cylinder bodies away from the turntable, and the distribution plate is fixed on the inner wall of the pump body at a certain inclination angle, and the distribution surface of the distribution plate is closely attached to the bottom surface of the cylinder body;

The pump body includes a front pump body and a rear pump body, bearings are arranged between the front pump body, the rear pump body and the main shaft, and a shaft seal is also arranged between the front pump body and the main shaft; there are 26 thin rod plungers, 13 on each side of the turntable, and they are symmetrically installed and arranged on both sides of the turntable;

A plurality of oil through holes connected to the cylinder hole are arranged on a surface of the cylinder body away from the turntable, and an oil suction waist-shaped through hole and an oil discharge waist-shaped through hole are arranged on the distribution plate. The plurality of oil through holes are connected to the oil suction waist-shaped through hole and the oil discharge waist-shaped through hole on the distribution plate, an oil inlet and an oil outlet are arranged on the pump body, and an oil inlet flow channel and an oil outlet flow channel are arranged inside the pump body, and two ends of the oil inlet flow channel are respectively connected to the oil suction waist-shaped through hole of the distribution plate on both sides, and two ends of the oil outlet flow channel are respectively connected to the oil discharge waist-shaped through hole of the distribution plate on both sides.

The ball joint is a cylindrical pin type ball joint, three synchronous cylindrical pins are fixed on the outside of the cylindrical pin type ball joint, and an arc groove track corresponding to the three synchronous cylindrical pins is provided on the inner wall of the cylinder body. The synchronous cylindrical pin is located in the arc groove track, and the main shaft drives the cylindrical pin type ball joint to rotate, and the torque is transmitted through the cooperation of the synchronous cylindrical pin and the arc groove track to drive the cylinder body to rotate.

The ball joint is a three-pivot ball joint, three pivots are fixed on the outer side of the three-pivot ball joint, spherical rollers are installed on the three pivots, a groove track corresponding to the spherical roller is provided on the inner wall of the cylinder body, the spherical roller is located in the groove track, the main shaft drives the three-pivot ball joint to rotate, and the torque is transmitted through the cooperation of the spherical roller and the groove track to drive the cylinder body to rotate.

The ball joint is a curved groove roller type ball joint, and a plurality of curved grooves are provided on the outer side of the curved groove roller type ball joint, and a retaining frame is sleeved on the outer side of the curved groove roller type ball joint, and a corresponding waist-shaped through hole is opened on the retaining frame, and balls are provided in the curved grooves of the curved groove roller type ball joint and the waist-shaped through hole of the retaining frame, and a plurality of curved rollers corresponding to the balls are provided on the three inner walls of the cylinder body, and the balls are located in the curved rollers, and the main shaft drives the curved groove roller type ball joint to rotate, and the torque is transmitted through the cooperation of the balls and the curved rollers to drive the cylinder body to rotate.

The ball joint is a linear groove and roller type ball joint, and a plurality of linear grooves are arranged on the outer side of the linear groove and roller type ball joint, and a retaining frame is sleeved on the outer side of the linear groove and roller type ball joint, and a corresponding waist-shaped through hole is opened on the retaining frame, and balls are arranged in the linear grooves of the linear groove and roller type ball joint and the waist-shaped through holes of the retaining frame, and a plurality of linear rollers corresponding to the balls are arranged on the four inner walls of the cylinder body, and the balls are located in the linear rollers, and the main shaft drives the linear groove and roller type ball joint to rotate, and the torque is transmitted through the cooperation of the balls and the linear rollers to drive the cylinder body to rotate.

The main shaft and the turntable are integrally formed, and an annular groove is opened on the end face of the ball joint close to the turntable. A limit plate is connected to the main shaft through a spline. The outer portion of the limit plate is stepped, and the end with a small outer diameter of the limit plate is located in the annular groove of the ball joint. A center spring is connected between the end with a large outer diameter of the limit plate and the end face of the ball joint, and a tool retraction groove is provided on the main shaft near the limit plate.

The cylindrical pin type ball joint, three-pivot type ball joint, curved groove raceway type ball joint, and linear groove raceway type ball joint are connected to the main shaft via splines;

The outer side surfaces of the cylindrical pin ball joint, three-pivot ball joint, curved groove roller type ball joint and linear groove roller type ball joint are all spherical or partially spherical, and the corresponding middle through holes of cylinder body one, cylinder body two, cylinder body three and cylinder body four contain a section of spherical surface. The outer spherical surfaces of the cylindrical pin ball joint, three-pivot ball joint, curved groove roller type ball joint and linear groove roller type ball joint are in mating contact with the spherical surfaces of the corresponding middle through holes of cylinder body one, cylinder body two, cylinder body three and cylinder body four.

When the spindle and the ball joint are integrally formed, a plurality of long cylindrical pins are installed on the outer side of the ball joint, and a linear groove track corresponding to the long cylindrical pins is provided on the inner wall of the middle through hole of the cylinder body 5 corresponding thereto, and the other end of the long cylindrical pin is located in the linear groove track. When the ball joint integral with the spindle rotates, the long cylindrical pin and the linear groove track cooperate to transmit torque, thereby driving the cylinder body 5 to rotate; the inner wall of the middle through hole of the cylinder body 5 is a cylindrical surface, and does not contain a spherical surface;

An annular groove 2 is opened at the bottom of the cylinder body 5, and a limiting disk 2, a center spring and a fixed disk are installed in the annular groove 2 in sequence. The fixed disk is fixedly connected to the cylinder body. The outer diameter of the limiting disk 2 is smaller than the annular groove 2. The inner spherical surface of the limiting disk 2 matches the spherical surface of the ball joint, and the outer part is stepped. The center spring is installed on the outside of the limiting disk 2 and is limited by the fixed disk.

Pressure plates are fixed on both sides of the turntable, and through holes corresponding to the ball sockets are opened on the pressure plates. The through holes match the outer surface of the thin rod plunger ball head, so that the thin rod plunger ball head is hinged on the turntable ball socket.

When the main shaft and the ball joint are integrally formed, the pressing plate is a split type, and the pressing plate is composed of two semicircular pressing plates;

When the main shaft and the ball joint are formed in one piece, the main shaft is split, and the split main shaft is respectively installed on both sides of the turntable.

The floating swash plate axial piston pump with a symmetrically inclined rotating assembly proposed in the utility model has the following new structural and technical advantages compared with the existing traditional axial piston pumps, floating cup pumps and previously designed floating swash plate axial piston pumps:

1. The two sets of rotating components of the utility model are respectively arranged at the two ends of the pump body cavity in an axisymmetric manner. The oil suction and oil discharge of the two sets of rotating components are respectively achieved through the designed oil suction flow channel and oil discharge flow channel in the pump body to achieve confluence, that is, an oil inlet flow channel and an oil outlet flow channel are provided inside the pump body, and the two ends of the oil inlet flow channel are respectively connected to the oil suction waist-shaped through holes of the distribution plate on both sides, and the two ends of the oil outlet flow channel are respectively connected to the oil discharge waist-shaped through holes of the distribution plate on both sides;

2. The number of plungers in the utility model is significantly increased, which is more than twice the number of plungers in the existing traditional axial piston pump and the previous floating swash plate axial piston pump, and is 2 more than the number of plungers in the existing floating cup pump, which can more significantly reduce the flow pulsation, pressure pulsation and vibration noise of the pump;

3. Compared with the existing traditional axial piston pump and floating cup pump, the utility model has a thin rod plunger with two ends that are rotating discs and cylinder bodies that rotate synchronously with the main shaft at a completely constant speed. Therefore, it is not necessary to transmit torque to drive the cylinder body through the plunger. Therefore, the side of the plunger does not need to contact the cylinder hole. Therefore, it is designed as a thin rod plunger. In this way, the plunger pair has basically no lateral force and friction at any time.

4. The plunger of the utility model is arranged axially symmetrically, and the axial force generated by the oil pressure in the plunger cavity can be completely offset in the pump body cavity; while the axial force of the existing traditional axial piston pump and the floating swash plate axial piston pump designed previously cannot be offset, but is transmitted to the housing through the swash plate, and is finally borne by the screws on the flange that fixes the pump;

5. The utility model is designed to be a floating swash plate axial piston pump with a symmetrically inclined rotating assembly. The plunger is a thin rod plunger, which is hinged to the turntable of the main shaft through the plunger ball head, that is, relative to the main shaft, the thin rod plunger has the freedom of swinging motion, and the cylinder body is an integral cylinder body, which solves the friction problem between the floating cup body and the split cylinder body existing in the existing floating cup pump;

6. The variable control of the utility model is more complicated than that of the existing traditional axial piston pump and the previously designed floating swash plate axial piston pump, which is equivalent to a floating cup pump. Relatively speaking, the floating swash plate axial piston pump with a symmetrically inclined rotating component in the utility model is more suitable for use as a fixed displacement pump, while the floating swash plate axial piston pump proposed in the previous patent is more suitable for use as a variable displacement pump.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is a cross-sectional view of the middle part of the first embodiment of the utility model;

FIG2 is a cross-sectional view of the front side of the first embodiment of the present invention;

FIG3 is a schematic diagram of the internal structure of the first embodiment of the present utility model;

FIG. 4 is a schematic diagram of the main shaft and turntable structure of the first embodiment of the utility model

Figure 5 is a schematic diagram of the main shaft, ball joint, and cylinder installation structure of Example 1 of the utility model; (Figure 5a is a cross-sectional view of a cylindrical pin type ball joint, Figure 5b is a cross-sectional view of a three-pivot type ball joint, Figure 5c is a cross-sectional view of a curved groove raceway type ball joint, Figure 5d is a cross-sectional view of a linear groove raceway type ball joint, Figure 5e is an overall appearance view of a cylindrical pin type ball joint, Figure 5f is an overall appearance view of a three-pivot type ball joint, Figure 5g is an overall appearance view of a curved groove raceway type ball joint, and Figure 5h is an overall appearance view of a linear groove raceway type ball joint).

FIG6 is a schematic diagram of the structure of a pressure plate in accordance with an embodiment of the present invention;

Figure 7 is a schematic diagram of the structure of the distribution plate of the utility model;

FIG8 is a front view of the distribution plate of the utility model;

FIG9 is a schematic diagram of the structure of a limiting plate according to an embodiment of the present utility model;

Figure 10 is a schematic diagram of the oil-passing hole structure of the cylinder body of the utility model;

FIG11 is a schematic diagram of the structure of a cylindrical pin-type ball joint of a spindle turntable according to a second embodiment of the utility model;

FIG12 is a schematic diagram of the cylinder body and ball joint structure of the second embodiment of the utility model;

FIG13 is a schematic diagram of the structure of the second limiting plate of the second embodiment of the utility model;

FIG14 is an exploded view of the installation of the second limiting plate and the cylinder body in the second embodiment of the utility model;

Figure 15 is a schematic diagram of the installation of the main shaft and the pressure plate in the second embodiment of the utility model, and the pressure plate is a split type;

FIG16 is a schematic diagram of the installation of the main shaft and the pressure plate in the second embodiment of the utility model, where the main shaft is a split type;

FIG. 17 is a schematic diagram of a main shaft cylindrical pin type ball joint body and a main shaft split structure in Embodiment 2 of the present utility model.

Numbers in the figure:

1 spindle, 2 turntable, 3 shaft seal, 4 bearing, 5 distribution plate, 6 ball joint, 6.1 cylindrical pin ball joint, 6.2 three-pivot ball joint, 6.3 curved groove roller type ball joint, 6.4 straight groove roller type ball joint, 7 cylinder body, 7.1 cylinder body one, 7.2 cylinder body two, 7.3 cylinder body three, 7.4 cylinder body four, 7.5 cylinder body five, 8 thin rod plunger, 9 pressure plate, 10.1 limit plate one, 10.2 limit plate 2. 11 fixed plate, 12 center spring, 13.1 synchronous cylindrical pin, 13.2 spherical roller, 13.3 ball, 13.4 long cylindrical pin, 13.5 cage, 14 oil inlet, 15 oil outlet, 16 oil inlet channel, 17 oil outlet channel, 18 oil through hole, 19 oil suction waist-shaped through hole, 20 oil discharge waist-shaped through hole, 21 ball socket, 22 cylinder hole, 23 back cutter groove, 24 front pump body, 25 rear pump body.

Detailed ways

Embodiment 1:

The first embodiment of the present invention discloses a floating inclined plate axial piston pump with a symmetrical tilted rotating assembly, as shown in Figures 1-4, including a front pump body 24, a rear pump body 25 and a main shaft 1 installed therein, the front side of the front pump body 24 is the cavity opening of the inner cavity, a shaft seal 3 is installed in the cavity opening, and the rear side is connected to the rear pump body 25. The inner cavity of the pump is sequentially installed with a bearing 4, a distribution plate 5, a cylinder body 7, a ball joint 6, a limit plate 10.1, a turntable 2, a limit plate 10.1, a ball joint 6, a cylinder body 7, a distribution plate 5, and a bearing 4, which are axially symmetrically distributed with the turntable 2 as the center. Among them: the front pump body 24, the rear pump body 25, the bearing 4, the ball joint 6, and the limit plate 10.1 are all in the front and rear directions, and the front section of the outer ring of the bearing 4 is fixed to the front pump body 24 and the front end of the main shaft 1. The central axis of the mounting surface of the distribution plate 5 inside the front pump body 24 and the rear pump body 25 is at an acute angle compared to the straight line in the front and rear directions.

An integrally formed turntable 2 is provided on the main shaft 1, and the same number of ball sockets 21 are symmetrically provided on two side surfaces of the turntable 2. Ball joints 6 are spline-connected on both sides of the turntable 2 on the main shaft 1, and corresponding cylinder bodies 7 are sleeved on the corresponding ball joints 6. A plurality of cylinder holes 22 are provided on a side of each cylinder body 7 close to the turntable 2, and the cylinder holes 22 correspond to the ball sockets 21 one by one. A thin rod plunger 8 is provided in each cylinder hole 22, and the end plunger ball head of the thin rod plunger 8 is hingedly installed on the ball socket 21, and the other end is placed in the cylinder hole 22. A distribution plate 5 is provided on the side of the two cylinder bodies 7 away from the turntable 2, and the distribution plate 5 is fixed to the inner wall of the pump body, and the distribution plate 5 is sealed and tightly attached to the cylinder body 7.

The total number of the thin rod plungers is typically one of 14, 18, 22, 26, and 30, and they are symmetrically installed and arranged on both sides of the turntable. The utility model uses 26 thin rod plungers, 13 of which are arranged on both sides of the turntable 2. The pump source flow pulsation and pressure pulsation of the pump will be greatly reduced, and the vibration noise of the pump will be effectively reduced.

As shown in Figure 5, Figure 5a shows that when the ball joint is a cylindrical pin type ball joint 6.1, the main shaft 1 is dragged and rotated by the prime mover, and the rotating main shaft 1 drives the cylindrical pin type ball joint 6.1 and the cylinder body 7.1 to rotate synchronously through the spline connection. One end of the synchronous cylindrical pin 13.1 is installed on the cylindrical pin type ball joint 6.1, and rotates synchronously with the rotation of the cylindrical pin type ball joint 6.1, and the other end is installed in the arc groove track of the cylinder body 7.1. Therefore, the synchronous cylindrical pin 13.1 driven by the cylindrical pin type ball joint 6.1 will contact the arc groove track of the cylinder body 7.1 and transmit torque, thereby driving the cylinder body 7.1 to rotate synchronously with the main shaft 1 at a quasi-constant speed.

Fig. 5b shows that when the ball joint is a three-pivot ball joint 6.2, the main shaft 1 is dragged and rotated by the prime mover, and the rotating main shaft 1 drives the three-pivot ball joint 6.2 and the cylinder body 2 7.2 to rotate synchronously through the spline connection, and the spherical roller 13.2 movably mounted on the three-pivot rotates synchronously with the rotation of the three-pivot ball joint 6.2, and the spherical roller 13.2 is embedded in the groove track of the cylinder body 2 7.2, so the spherical surface of the spherical roller 13.2 driven by the three-pivot ball joint 6.2 will contact the groove track of the cylinder body 2 7.2 and transmit torque, thereby driving the cylinder body 2 7.2 to rotate. The spherical roller 13.2 can make the axis of the pivot on which it is located intersect with the axis of the corresponding groove track on the cylinder body 7.2. When the intersection angle between the main shaft 1 and the central axis of the cylinder body 7.2 is not 0, because the spherical roller can move along the pivot axis at the same time, it can also slide along the corresponding groove track, so that the spherical surface of the spherical roller 13.2 and the groove surface of the corresponding groove track of the cylinder body 7.2 fit together. The contact generatrix formed by the two can ensure that the force transmission point of the spherical roller 13.2 is always located on the bisector of the intersection angle between the main shaft 1 and the central axis of the cylinder body 7.2. Therefore, it has a constant speed transmission characteristic, which ensures that power can always be transmitted between the main shaft 1 and the cylinder body 7.2, and it is always a constant speed transmission.

Fig. 5c shows that when the ball joint is a curved groove raceway type ball joint 6.3, the main shaft 1 is dragged and rotated by the prime mover, and the rotating main shaft 1 drives the curved groove raceway type ball joint 6.3 to rotate synchronously through the spline connection, and the ball 13.3 clamped in the waist-shaped through hole of the retaining frame 13.5 can roll freely between the curved groove on the curved groove raceway type ball joint 6.3 and the curved raceway on the cylinder body three 7.3. When the intersection angle of the central axis between the cylinder body three 7.3 and the curved groove raceway type ball joint 6.3 is constant, the ball 13.3 clamped in the waist-shaped through hole of the retaining frame 13.5 is positioned by the cross action of the curved groove on the curved groove raceway type ball joint 6.3 and the curved raceway on the cylinder body three 7.3, and the force and torque are transmitted between the curved groove raceway type ball joint 6.3 and the cylinder body three 7.3 by the ball 13.3. The cage 13.5 has an inner spherical surface and an outer spherical surface. The inner spherical surface of the cage 13.5 is in contact with the spherical outer surface of the curved groove raceway type ball joint 6.3, and the outer spherical surface of the cage 13.5 is in contact with the spherical surface of the cylinder body 3 7.3, that is, the cylinder body 3 7.3 is supported on the curved groove raceway type ball joint 6.3 through the spherical contact effect and the ball contact effect. The centers of all the balls 13.3 are located on the bisector of the angle between the central axes of the curved groove raceway type ball joint 6.3 and the cylinder body 3 7.3, so the curved groove raceway type ball joint 6.3 can synchronously drive the cylinder body 3 7.3 to rotate at a constant speed.

Figure 5d shows that when the ball joint is a linear groove and roller type ball joint 6.4, the main shaft 1 is dragged and rotated by the prime mover, and the rotating main shaft 1 drives the linear groove and roller type ball joint 6.4 to rotate synchronously through the spline connection. The ball 13.3 clamped in the waist-shaped through hole of the retaining frame 13.5 can roll freely between the linear groove on the linear groove and roller type ball joint 6.4 and the linear roller on the cylinder body 7.4. When the intersection angle of the central axis between the cylinder body 7.4 and the linear groove and roller type ball joint 6.4 is constant, the ball 13.3 clamped in the waist-shaped through hole of the retaining frame 13.5 is positioned by the cross action of the linear groove on the linear groove and roller type ball joint 6.4 and the linear roller on the cylinder body 7.4, and the force and torque are transmitted between the linear groove and roller type ball joint 6.4 and the cylinder body 7.4 by the ball 13.3. The cage 13.5 has an inner spherical surface and an outer spherical surface. The inner spherical surface of the cage 13.5 is in contact with the spherical outer surface of the linear groove roller type ball joint 6.4, and the outer spherical surface of the cage 13.5 is in contact with the spherical surface of the middle through hole of the cylinder body 4 7.4, that is, the cylinder body 4 7.4 is supported on the linear groove roller type ball joint 6.4 through the contact action of the spherical surface and the contact action of the balls 13.3. The centers of all the balls 13.3 are located on the bisector of the angle between the central axes of the linear groove roller type ball joint 6.4 and the cylinder body 4 7.4, so the linear groove roller type ball joint 6.4 can synchronously drive the cylinder body 4 7.4 to rotate at a constant speed, and axial displacement is also allowed, that is, the balls 13.3 can roll axially on the linear roller, and the axial movement caused by the working and installation errors between the linear groove roller type ball joint 6.4 and the cylinder body 4 7.4 can be compensated.

The cylindrical pin type ball joint 6.1, the three-pivot type ball joint 6.2, the curved groove raceway type ball joint 6.3, and the linear groove raceway type ball joint 6.4 are connected to the main shaft 1 via splines.

The outer side surfaces of the cylindrical pin ball joint 6.1, three-pivot ball joint 6.2, curved groove roller type ball joint 6.3, and linear groove roller type ball joint 6.4 are all spherical surfaces or partially spherical surfaces, and the corresponding middle through holes of the cylinder body 1 7.1, cylinder body 2 7.2, cylinder body 3 7.3, and cylinder body 4 7.4 contain a spherical surface, and the outer spherical surfaces of the cylindrical pin ball joint 6.1, three-pivot ball joint 6.2, curved groove roller type ball joint 6.3, and linear groove roller type ball joint 6.4 are in contact with the spherical surfaces of the corresponding middle through holes of the cylinder body 1 7.1, cylinder body 2 7.2, cylinder body 3 7.3, and cylinder body 4 7.4.

As shown in Figs. 2, 7, 8 and 10, a plurality of oil-passing holes 18 communicating with the cylinder hole 22 are provided on the side of the cylinder body 7 away from the rotary disk 2, and an oil-intake waist-shaped through hole 19 and an oil-discharge waist-shaped through hole 20 are provided on the distribution plate 5. The plurality of oil-passing holes 18 are communicated with the oil-intake waist-shaped through hole 19 and the oil-discharge waist-shaped through hole 20 on the distribution plate, an oil inlet 14 and an oil outlet 15 are provided on the pump body, and an oil inlet flow channel 16 and an oil outlet flow channel 17 are provided inside the pump body, and the two ends of the oil inlet flow channel 16 are respectively communicated with the oil-intake waist-shaped through hole 19 of the distribution plate 5 on both sides, and the two ends of the oil outlet flow channel 17 are respectively communicated with the oil-discharge waist-shaped through hole 20 of the distribution plate 5 on both sides. The oil in the oil-intake waist-shaped through hole 19 is discharged through the oil-discharge waist-shaped through hole 20 by the rotation of the cylinder body 7. The hydraulic oil at the oil inlet 14 passes through the oil inlet flow channel 16 and enters the oil suction waist-shaped through hole 19 of the distribution plate 5, then enters the oil through hole 18 of the cylinder body 7, and then enters the cylinder hole 22. The low-pressure oil is rotated and compressed by the thin rod plunger 8 to become high-pressure oil. The high-pressure oil then passes through the oil through hole 18 and the oil discharge waist-shaped through hole 20 of the distribution plate 5, enters the oil outlet flow channel 17, and is then delivered from the oil outlet 15.

As shown in Figs. 5 and 9, an annular groove is formed on the end surface of the ball joint 6 near the turntable 2, and a limit plate 10.1 is connected to the main shaft 1 through a spline. The outer portion of the limit plate 10.1 is stepped, and the end with a smaller outer diameter of the limit plate 10.1 is located in the annular groove of the ball joint 6. A moment spring 12 is connected between the end with a larger outer diameter of the limit plate 10.1 and the end surface of the ball joint 6, and a knife-retracting groove 23 is provided on the main shaft 1 near the limit plate 10.1. The diameter of the knife-retracting groove 23 is larger than the diameter of the limit plate 10.1, so that the limit plate 10.1 cannot move to the right. A center spring 12 is installed between the limit plate 10.1 and the ball joint 6, and one end of the center spring 12 acts on the limit plate 10.1, and the other end acts on the ball joint 6 and presses against the cylinder body 7, so that the cylinder body 7 presses against the distribution plate 5, providing an initial preload force for the distribution pair.

As shown in FIG6 , pressure plates 9 are fixed on both sides of the turntable 2, and through holes corresponding to the ball sockets 21 are opened on the pressure plates 9, and the through holes match the outer surface of the thin rod plunger 8. The pressure plates 9 can prevent the plunger ball head from falling, so that the plunger ball head of the thin rod plunger 8 is hinged on the ball socket 21 of the turntable 2.

The pressing plate 9 is fixedly connected to the rotating disk 2 by bolts.

Embodiment 2:

As shown in Figures 11-17, a floating swash plate axial piston pump with a symmetrical tilted rotating assembly includes a front pump body 24, a rear pump body 25 and a main shaft 1 installed therein. The front side of the front pump body 24 is the cavity opening of the inner cavity, a shaft seal 3 is installed in the cavity opening, and the rear side is connected to the rear pump body 25. The inner cavity of the pump is installed with bearings 4, a distribution plate 5, a cylinder body 7, a rotating disk 2, a cylinder body 7, a distribution plate 5, and a bearing 4 in sequence, and is axially symmetrically distributed with the rotating disk 2 as the center. Among them: the front pump body 24, the rear pump body 25, and the bearing 4 are all in the front-to-back direction, and the front section of the outer ring of the bearing 4 is fixed to the front pump body 24 and the front end of the main shaft 1. The central axis of the installation surface of the distribution plate 5 inside the front pump body 24 and the rear pump body 25 is at an acute angle compared to the straight line in the front-to-back direction.

The main shaft 1 and the ball joint 6 are integrally formed. The main shaft 1 is rotated by the prime mover. The rotating main shaft 1 rotates synchronously by driving the long cylindrical pin 13.4. The other end of the long cylindrical pin 13.4 is installed in the linear groove track of the cylinder body 5 7.5. Therefore, the driven long cylindrical pin 13.4 contacts the linear groove track on the cylinder body 5 7.5 and transmits torque, thereby driving the cylinder body 5 7.5 to rotate synchronously with the main shaft 1 at a quasi-constant speed.

As shown in Figures 13-14: an annular groove is opened at the bottom of the cylinder body 5 7.5, and a limit plate 2 10.2, a center spring 12, and a fixed plate 11 are installed in sequence. The outer diameter of the limit plate 2 10.2 is smaller than the annular groove 2, and the inner spherical surface of the limit plate 2 10.2 cooperates with the ball joint 6, and the outer part is stepped. The center spring 12 is installed on the outside of the limit plate 2 10.2 and is limited by the fixed plate 11. The fixed plate 11 is installed on the inner bottom surface of the cylinder body 5 7.5 by bolts, and the bolt installation surface is lower than the distribution surface. One end of the center spring 12 acts on the limit plate 2 10.2 and acts on the ball joint part, and the other end acts on the fixed plate 11 and is transmitted to the cylinder body 5 7.5, so that the cylinder body 5 7.5 is pressed against the distribution plate 5 to provide an initial preload for the distribution pair.

As shown in FIG. 15 , when the spindle 1 , the turntable 2 , and the ball joint 6 are integrally formed, the pressure plate 9 is a split type, and the pressure plate 9 is composed of two semicircular pressure plates.

As shown in FIGS. 16 and 17 , when the main shaft 1 and the ball joint 6 are formed as one piece, the main shaft 1 is a split type, and the split main shaft is respectively installed on both sides of the turntable 2 .

Claims (10)

1. A floating inclined plate axial piston pump with a symmetrically inclined rotating component, characterized in that it includes a pump body, a main shaft is installed in the pump body, a turntable is installed on the main shaft, the same number of ball sockets are symmetrically arranged on two sides of the turntable, and ball joints are splined or integrally formed on the main shaft on both sides of the turntable, a cylinder body is installed on the outside of each ball joint, and a plurality of cylinder holes are arranged on a surface of each cylinder body close to the turntable, the cylinder holes correspond to the ball sockets one by one, a thin rod plunger is arranged in each cylinder hole, the end plunger ball head of the thin rod plunger extends out of the cylinder hole and extends into the ball socket of the turntable corresponding to it, a distribution plate is arranged on the side of the two cylinder bodies away from the turntable, the distribution plate is fixed to the inner wall of the pump body at a certain inclination angle, and the distribution surface of the distribution plate is close to the bottom surface of the cylinder body; The pump body includes a front pump body and a rear pump body, bearings are arranged between the front pump body, the rear pump body and the main shaft, and a shaft seal is also arranged between the front pump body and the main shaft; there are 26 thin rod plungers, 13 on each side of the turntable, and they are symmetrically installed and arranged on both sides of the turntable; A plurality of oil through holes connected to the cylinder hole are arranged on a surface of the cylinder body away from the turntable, and an oil suction waist-shaped through hole and an oil discharge waist-shaped through hole are arranged on the distribution plate. The plurality of oil through holes are connected to the oil suction waist-shaped through hole and the oil discharge waist-shaped through hole on the distribution plate, an oil inlet and an oil outlet are arranged on the pump body, and an oil inlet flow channel and an oil outlet flow channel are arranged inside the pump body, and two ends of the oil inlet flow channel are respectively connected to the oil suction waist-shaped through hole of the distribution plate on both sides, and two ends of the oil outlet flow channel are respectively connected to the oil discharge waist-shaped through hole of the distribution plate on both sides. 2. According to claim 1, a floating swash plate axial piston pump with a symmetrical inclined rotating assembly is characterized in that: the ball joint is a cylindrical pin type ball joint, three synchronous cylindrical pins are fixed to the outside of the cylindrical pin type ball joint, and an arc groove track corresponding to the three synchronous cylindrical pins is provided on the inner wall of the cylinder body, and the synchronous cylindrical pin is located in the arc groove track. The main shaft drives the cylindrical pin type ball joint to rotate, and the torque is transmitted through the cooperation of the synchronous cylindrical pin and the arc groove track to drive the cylinder body to rotate. 3. A floating swash plate axial piston pump with a symmetrically inclined rotating assembly according to claim 2, characterized in that: the ball joint is a three-pivot ball joint, three pivots are fixed on the outer side of the three-pivot ball joint, spherical rollers are installed on the three pivots, and a groove track corresponding to the spherical roller is provided on the inner wall of the cylinder body, the spherical roller is located in the groove track, the main shaft drives the three-pivot ball joint to rotate, and the torque is transmitted through the cooperation of the spherical roller and the groove track to drive the cylinder body to rotate. 4. A floating swash plate axial piston pump with a symmetrically inclined rotating component according to claim 3, characterized in that: the ball joint is a curved groove roller type ball joint, a plurality of curved grooves are provided on the outer side of the curved groove roller type ball joint, a retaining frame is sleeved on the outer side of the curved groove roller type ball joint, a corresponding waist-shaped through hole is opened on the retaining frame, balls are provided in the curved grooves of the curved groove roller type ball joint and the waist-shaped through holes of the retaining frame, a plurality of curved rollers corresponding to the balls are provided on the three inner walls of the cylinder body, the balls are located in the curved rollers, the main shaft drives the curved groove roller type ball joint to rotate, and the torque is transmitted through the cooperation of the balls and the curved rollers to drive the cylinder body to rotate. 5. A floating swash plate axial piston pump with a symmetrically inclined rotating component according to claim 4, characterized in that: the ball joint is a linear groove and roller type ball joint, a plurality of linear grooves are provided on the outer side of the linear groove and roller type ball joint, a retaining frame is sleeved on the outer side of the linear groove and roller type ball joint, a corresponding waist-shaped through hole is opened on the retaining frame, balls are provided in the linear grooves of the linear groove and roller type ball joint and the waist-shaped through holes of the retaining frame, a plurality of linear rollers corresponding to the balls are provided on the four inner walls of the cylinder body, the balls are located in the linear rollers, the main shaft drives the linear groove and roller type ball joint to rotate, and the torque is transmitted through the cooperation of the balls and the linear rollers to drive the cylinder body to rotate. 6. A floating inclined plate axial piston pump with a symmetrical inclined rotating component according to claim 1, characterized in that: the main shaft and the turntable are integrally formed, an annular groove is opened on the end face of the ball joint close to the turntable, a limit plate is connected to the main shaft through a spline, the outer portion of the limit plate is stepped, the end of the limit plate with a small outer diameter is located in the annular groove of the ball joint, a center spring is connected between the end of the limit plate with a large outer diameter and the end face of the ball joint, and a back-off groove is provided on the main shaft near the limit plate. 7. A floating swash plate axial piston pump with a symmetrical tilting rotating assembly according to claim 5, characterized in that: the cylindrical pin type ball joint, three-pivot type ball joint, curved groove roller type ball joint, and linear groove roller type ball joint are connected to the main shaft through a spline; The outer side surfaces of the cylindrical pin ball joint, three-pivot ball joint, curved groove roller type ball joint and linear groove roller type ball joint are all spherical or partially spherical, and the corresponding middle through holes of cylinder body one, cylinder body two, cylinder body three and cylinder body four contain a section of spherical surface. The outer spherical surfaces of the cylindrical pin ball joint, three-pivot ball joint, curved groove roller type ball joint and linear groove roller type ball joint are in mating contact with the spherical surfaces of the corresponding middle through holes of cylinder body one, cylinder body two, cylinder body three and cylinder body four. 8. A floating swash plate axial piston pump with a symmetrical tilted rotating assembly according to claim 1, characterized in that: when the main shaft and the ball joint are integrally formed, a plurality of long cylindrical pins are installed on the outer side of the ball joint, and a linear groove track corresponding to the long cylindrical pins is provided on the inner wall of the middle through hole of the cylinder body corresponding thereto, and the other end of the long cylindrical pin is located in the linear groove track, and when the ball joint integral with the main shaft rotates, the long cylindrical pin and the linear groove track cooperate to transmit torque, driving the cylinder body five to rotate; the inner wall of the middle through hole of the cylinder body five is a cylindrical surface, without a spherical surface; An annular groove 2 is opened at the bottom of the cylinder body 5, and a limiting disk 2, a center spring and a fixed disk are installed in the annular groove 2 in sequence. The fixed disk is fixedly connected to the cylinder body. The outer diameter of the limiting disk 2 is smaller than the annular groove 2. The inner spherical surface of the limiting disk 2 matches the spherical surface of the ball joint, and the outer part is stepped. The center spring is installed on the outside of the limiting disk 2 and is limited by the fixed disk. 9. According to claim 1, a floating inclined plate axial piston pump with a symmetrical inclined rotating component is characterized in that: pressure plates are respectively fixed on both side surfaces of the turntable, and through holes corresponding to the ball sockets are opened on the pressure plates, and the through holes match the outer surface of the thin rod plunger ball head, so that the thin rod plunger ball head is hinged on the turntable ball socket. 10. A floating swash plate axial piston pump with a symmetrically inclined rotating assembly according to claim 9, characterized in that: when the main shaft and the ball joint are integrally formed, the pressure plate is a split type, and the pressure plate is composed of two semicircular pressure plates; When the main shaft and the ball joint are formed in one piece, the main shaft is split, and the split main shaft is respectively installed on both sides of the turntable.