A floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate

Abstract

The present invention discloses a floating swash plate type conical plunger variable pump rotating assembly without a pressure plate, comprising a cylinder body, a rotary plate, a floating swash plate, a base, a main shaft and a plurality of conical plungers. The rotary plate assembly surface is rotatably mounted on the floating swash plate assembly surface, the conical plunger is mounted in the cylinder body, the conical plunger ball head is hinged to the ball socket of the rotary plate, and the main shaft passes through the cylinder body, the rotary plate, the floating swash plate and the base in sequence. The assembly surface of the rotary plate is provided with a ball socket with a micro cylindrical surface feature. When the cylindrical surface of the ball head is coaxial with the cylindrical surface of the ball socket, the plunger ball head can freely enter and exit the ball socket. When the cylindrical surface of the ball head is not coaxial with the cylindrical surface of the ball socket, the plunger ball head is snap-jointed to the ball socket in the form of a ball joint pair. The assembly surface of the floating swash plate is provided with a sealing belt that cooperates with the waist groove on the rotary plate to form a static pressure oil chamber. The present invention breaks through the traditional structure, reduces the friction and wear of the plunger pump from the fundamental structural principle within the full range of working conditions, reduces the cost and greatly improves the compactness of the structure.

Description

Technical Field

[0001] The invention relates to the field of inclined plate type conical plunger variable displacement pumps, in particular to a floating inclined plate type conical plunger variable displacement pump rotating assembly without a pressure plate. Background Art

[0002] Hydraulic technology accounts for a large proportion in the application of engineering machinery, and its advantages in heavy industry are particularly prominent. As the energy device of the hydraulic system, the hydraulic pump is the most important power component in the entire system, which greatly affects the quality of the system. Various application fields have higher and higher requirements for the control performance and control flexibility of variable hydraulic pumps. The axial piston variable pump has been widely used in metallurgy, mining, engineering machinery, ships and other fields due to its high pressure level, low noise and stable operation.

[0003] In recent years, with the continuous development of science and technology, various industries have also put forward more stringent requirements for the performance of plunger pumps. With the increasingly urgent demand for high pressure, high speed and high performance, it is urgent to solve the problem of wear resistance and life extension of axial piston pumps. The plunger pair and the slipper pair are important friction pairs of the inclined plate piston pump. The friction generated by the two friction pairs is an important part of the power loss of the inclined plate piston pump. On the one hand, the relative sliding between the friction pair elements, if the lubrication condition is poor, the gap is too small or even long-term solid contact, is very easy to generate heat accumulation, which will accelerate wear and reduce life and increase mechanical losses, or even directly sinter and damage; on the other hand, if the gap between the friction elements is too large, the sealing effect of the friction pair will be reduced, the leakage will increase rapidly, thereby reducing the volumetric efficiency of the entire pump.

[0004] Therefore, the friction, wear and lubrication failure problems of the heavy-loaded friction pairs in the traditional swash plate axial piston pump are the main technical difficulties restricting the improvement of the performance of the swash plate axial piston. The technical means to improve the friction and wear resistance of the piston pair and the slipper pair of the swash plate axial piston pump have long been based on the optimization design of the lubrication support structure, the surface modification of the friction interface and the surface micro-modification technology. Although some important technical progress has been made, the problem has not been completely solved. Moreover, the traditional swash plate axial piston pump also has the disadvantages of complex structure and high requirements on materials and processing precision, which also brings severe challenges to the design of the piston pump. Therefore, more and more in-depth research is still needed on the technologies and methods of friction and wear resistance of the piston pump. Summary of the invention

[0005] The invention provides a floating swash plate type conical plunger variable pump rotating assembly without a pressure plate, so as to solve the problem of large friction and wear of the friction pair of the swash plate type axial plunger pump under heavy load in the prior art.

[0006] In order to achieve the above object, the technical solution adopted by the present invention is:

[0007] A floating swash plate type conical plunger variable pump rotating assembly without a pressure plate, comprising a cylinder body 3, a rotary plate 5, a floating swash plate 6, a base 9, a main shaft 1 and a plurality of conical plungers 4, wherein the rotary plate 5 is rotatably mounted on one side of the floating swash plate 6, with the opposite sides of the rotary plate 5 and the floating swash plate 6 serving as respective assembly surfaces, the other side of the rotary plate 5 facing the cylinder body 3, and the other side of the rotary plate 5 serving as a ball joint mounting surface, the ball joint mounting surface of the rotary plate 5 being provided with a plurality of ball sockets 16, a plurality of plunger cavities 21 being provided in the cylinder body 3, the conical plungers 4 being mounted in the plunger cavities 21 in a one-to-one correspondence, the ball head end of each conical plunger 4 respectively passing through one end of the plunger cavity 21 towards the rotary plate 5, and the ball heads of each conical plunger 4 being ball-jointed in the ball sockets 16 of the ball joint mounting surface of the rotary plate 5 in a one-to-one correspondence, the other end of each plunger cavity 21 being used for passing in or pressing out hydraulic oil, the main shaft 1 sequentially passing through the cylinder body 3, the rotary plate 5, floating swash plate 6, base 9, and the main shaft 1 is only fixedly connected to the cylinder body 3, when the main shaft 1 rotates, it drives the cylinder body 3 and each tapered plunger 4 to rotate as a whole, and drives the rotating plate 5 to rotate through the tapered plunger 4, characterized in that the assembly surface of the rotating plate 5 is provided with a plurality of grooves 17, and the rotating plate 5 is provided with a plurality of oil guide channels 19, the positions of the grooves 17 and the oil guide channels 19 are all corresponding to the ball sockets 16 one by one, and the orifices at one end of the oil guide channels 19 are connected to the ball sockets 16 at the corresponding positions, and the orifices at the other end are connected to the grooves 17 at the corresponding positions, and the assembly surface of the floating swash plate 6 is provided with an outer auxiliary support belt 14 and an inner auxiliary support belt 15 distributed in double rings, and a sealing belt 13 is provided on the assembly surface of the floating swash plate 6 between the outer auxiliary support belt 14 and the inner auxiliary support belt 15, and the sealing belt 13 is pressed on each groove 17 on the assembly surface of the rotating plate 5, and the sealing belt 13 cooperates with each groove 17 to form a static pressure oil chamber respectively;

[0008] The conical plunger 4 has a central through hole 24, one end of the central through hole 24 is connected to the corresponding plunger cavity 21, and the other end of the central through hole 24 is connected to the ball socket 16 at the corresponding position on the ball joint mounting surface of the turntable 5. The hydraulic oil in the plunger cavity 21 is introduced into the static pressure oil chamber through the central through hole 24 to form a static pressure support between the turntable 5 and the floating swash plate 6.

[0009] Furthermore, a ball joint 20 is movably installed on the side of the cylinder body 3 facing the turntable 5. The ball joint 20 is hinged to the through hole of the turntable 5 for the main shaft 1 to pass through. A plurality of spring holes 25 are also provided in the cylinder body 3. A spring 8 is installed in each spring hole 25. One end of each spring 8 passes through the spring hole 25 toward one end of the ball joint 20 and then presses against the ball joint 20.

[0010] Furthermore, each ball socket 16 mouth of the ball joint mounting surface of the turntable 5 is formed as a cylindrical mouth 18, and the circumferential outer surface of the ball head end of the tapered plunger 4 is formed with an annular groove 22. The central axis of the annular groove 22 is inclined at a certain angle compared to the central axis of the tapered plunger 4. The diameter of the annular groove 22 is smaller than the diameter of the cylindrical mouth 18. When the ball head end of the tapered plunger 4 is ball-jointed in the ball socket 16, the annular groove 22 and the cylindrical mouth 18 form a size match.

[0011] Furthermore, the material of the rotary plate 5 and the material of the floating swash plate 6 are tribologically compatible.

[0012] Furthermore, when the floating swash plate 6 is made of steel, the rotating plate 5 is made of pure copper.

[0013] Furthermore, when the floating swash plate 6 is made of steel, the rotating plate 5 uses carbon steel as a base material, and the assembly surface of the rotating plate 5 is a bimetallic composite material formed by a cast or sintered copper alloy.

[0014] Furthermore, when the rotary plate 5 is made of all-steel material, the floating swash plate 6 uses steel material as the base material, and the assembly surface of the floating swash plate 6 is made of molten copper bimetallic material.

[0015] Furthermore, a gasket is installed on the assembly surface of the floating swash plate 6, and the gasket replaces the assembly surface of the floating swash plate 6 facing the assembly surface of the rotating plate 5, and the outer auxiliary support belt 14, the inner auxiliary support belt 15, and the sealing belt 13 are all arranged on the side of the gasket facing the rotating plate 5.

[0016] The floating swash plate of the present invention is provided with a sealing belt and static pressure support structures such as inner and outer auxiliary support belts on the surface. An oil guide channel is provided in the middle of the upper groove of the rotating plate assembly surface. The pressure oil in the plunger cavity is drained into the upper groove of the rotating plate through the oil guide channel. Under the joint action of the sealing belt on the surface of the floating swash plate, the inner and outer auxiliary support belts and the rotating plate groove, the rotating plate is fully statically supported to balance the force of the plunger on the rotating plate, thereby improving the movement accuracy of the rotating plate and increasing the carrying capacity of the floating swash plate.

[0017] The floating swash plate assembly of the present invention does not require bearing support, can achieve full hydrostatic support, and completely avoids the complexity of parts caused by the opening of a bearing structure. Compared with the existing plunger pump structure, it reduces costs while greatly improving the compactness of the pump structure, increases the design freedom space of other components in the pump, and can effectively reduce the friction and wear between the floating swash plate and the rotary plate.

[0018] The material of the rotary plate of the present invention is tribologically compatible with the surface material of the floating swash plate. For light-load pumps, the rotary plate can be made of all copper; for heavy-load pumps, the rotary plate can be made of carbon steel as the base material, and the bottom surface of the rotary plate is cast or sintered with copper alloy to form a bimetallic composite material to enhance the comprehensive mechanical properties and friction reduction and wear resistance of the rotary plate.

[0019] The ball head end of the tapered plunger of the present invention is provided with an annular groove which is inclined at a certain angle (not 0°, not 180°) to the central axis of the tapered plunger, 9 ball sockets are evenly provided on the surface of the rotary disk, and a tiny cylindrical surface is provided at the top surface of the ball sockets. One end of the tapered plunger is installed in the cylinder hole of the cylinder body, and the ball head of the other end of the tapered plunger is hinged to the ball socket on the rotary plate in the form of a ball joint. When the cylindrical surface of the tapered plunger ball head and the cylindrical surface at the top of the ball socket remain parallel, that is, coaxial, the plunger ball head can be inserted into the rotary plate ball socket. After the plunger ball head enters the rotary plate ball socket, if the parallel geometric relationship between the cylindrical surface of the tapered plunger ball head and the cylindrical surface at the top of the ball socket is changed, that is, the coaxial geometric relationship is not present, the tapered plunger ball head is hinged in the rotary plate ball socket. During the operation of the plunger pump, even when the inclination angle of the swash plate is 0°, the plunger ball head can maintain an articulated relationship with the rotary plate ball socket and will not fall off, making the structure more compact, giving the cylinder body and the floating swash plate greater design flexibility and design space.

[0020] The floating swash plate of the present invention is wholly immersed in hydraulic oil during operation, and is fully lubricated and cooled. Moreover, due to the use of a hydrostatic bearing bearing form, a longer service life can be achieved through a reasonable design of the floating swash plate, and the floating swash plate is also easy to maintain and replace when wear occurs.

[0021] The conical plunger ball head of the present invention is snap-jointed to the ball socket on the rotating disk in the form of a ball joint pair, and only the spherical surface at the rear end contacts the plunger cavity wall of the cylinder body in a tangential form and forms a plunger pair, which greatly reduces the friction contact area of ​​the plunger pair and enables the conical plunger to form a two-force rod force condition, thereby achieving a significant reduction in the force between the plunger and the plunger cavity wall, thereby significantly reducing the friction force and friction power loss at the plunger pair, and solving the problem of severe friction wear of the plunger pair caused by the huge lateral force and torque on the plunger in the traditional fixed inclined plate axial piston pump. The metal sealing rings installed at the grooves on both sides of the conical plunger spherical surface can reduce the flow leakage at the plunger pair.

[0022] The cylinder body of the present invention is evenly provided with spring holes on the axial circumference. The spring is a compression spring. One end of the spring acts in the cylinder body hole, and the other end of the spring acts on the rotary plate through a ball joint. The main shaft is fixedly connected to the cylinder body through a key and drives the cylinder body to rotate. The cylinder body drives the conical plunger in the cylinder hole to rotate. The conical plunger ball head acts on the ball socket of the rotary plate and drives the rotary plate to produce a rotary motion on the inclined plate surface. When the pump oil pressure has not yet been established, the spring provides a return force for the conical plunger on the one hand, and on the other hand, pushes the cylinder body so that the cylinder body is pressed against the distribution plate and pushes the rotary plate so that the rotary plate is pressed tightly against the floating inclined plate surface, thereby ensuring the initial pre-sealing performance of the distribution pair and the rotary plate pair. It can be seen from the above that the present invention can reduce the friction and wear of the friction pair of the inclined plate type axial piston pump under heavy load within the full range of working conditions, improve the reliability and service life of the moving pair, and improve the efficiency performance of the pump.

[0023] The present invention breaks through the traditional structure and reduces the friction and wear of the friction pair of the inclined plate axial piston pump under heavy load from the fundamental structural principle within the entire working range, thereby reducing costs and greatly improving the compactness of the pump structure, thereby increasing the design freedom space for other components in the pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a forward assembly diagram of the structure of an embodiment of the present invention.

[0025] Figure 2 It is a rearward exploded view of the structure of an embodiment of the present invention.

[0026] Figure 3 It is a front view of the turntable structure in an embodiment of the present invention.

[0027] Figure 4 It is a rear view of the turntable structure in the embodiment of the present invention.

[0028] Figure 5 It is a side sectional view of the turntable structure in an embodiment of the present invention.

[0029] Figure 6 It is a rear view of the floating swash plate structure in the embodiment of the present invention.

[0030] Figure 7 It is a half-section view of the partial transfer structure of the cylinder body, rotating plate, inclined plate and base in an embodiment of the present invention.

[0031] Figure 8 It is a side sectional view of the partial transfer structure of the main shaft, cylinder body, rotary plate and inclined plate in an embodiment of the present invention.

[0032] Fig. 9 It is a cross-sectional view of the cylinder structure (including spring) in an embodiment of the present invention.

[0033] Fig.10 It is a side sectional view of the cylinder structure in an embodiment of the present invention.

[0034] Fig.11 It is a side sectional view of the tapered plunger structure in an embodiment of the present invention.

[0035] Fig.12 1 is a side view of a tapered plunger structure in an embodiment of the present invention.

[0036] Fig.13 Schematic diagram of the tapered plunger dimensions in an embodiment of the present invention.

[0037] Fig.14 yes Figure 5 A partial enlarged view of position A in the middle. DETAILED DESCRIPTION

[0038] The present invention is further described below in conjunction with the accompanying drawings and embodiments.

[0039] like Figure 1 , Figure 2 As shown, this embodiment discloses a floating swash plate type conical plunger variable pump rotating assembly without a pressure plate, including a flange 12, a bearing 10, a base 9, a floating swash plate 6, a rotating plate 5, a cylinder body 3, a distribution plate 2, a main shaft 1, and 9 conical plungers 4 distributed from front to back.

[0040] The axial directions of the flange 12, the bearing 10, the base 9, the cylinder body 3 and the valve plate 2 are all in the front-to-back horizontal direction, and there is a central through hole in the center of the flange 12, the bearing 10, the base 9, the cylinder body 3 and the valve plate 2. The floating swash plate 6 and the rotating plate 5 are in the same inclined posture, and there is also a central through hole in the center of the rotating plate 5 and the floating swash plate 6.

[0041] The front end of the bearing 10 is fixed to the rear side of the flange 12, and the base 9 is fixed to the rear end of the bearing 10 through its front end. The floating swash plate 6 is installed on the rear end of the base 9 through its front end, and the rear side disk surface of the floating swash plate 6 is opposite to the front side disk surface of the rotating plate 5, and the rotating plate 5 is rotatably installed on the rear side disk surface of the floating swash plate 6 through its front side disk surface, and the rear side disk surface of the floating swash plate 6 is used as the assembly surface of the floating swash plate 6, and the front side disk surface of the rotating plate 5 is used as the assembly surface of the rotating plate 5.

[0042] like Figure 3 , Figure 4 , Figure 5As shown, the rear side of the rotating disk 5 faces the front end of the cylinder body 3, and the rear side of the rotating disk 5 is provided with 9 ball sockets 16 as the ball joint mounting surface, and the 9 ball sockets 16 are evenly distributed around the central through hole of the rotating disk 5 at equal intervals in the circumferential direction. The assembly surface of the rotating disk 5 is provided with 9 waist-shaped grooves 17, and the positions of the 9 waist-shaped grooves 17 correspond to the ball sockets 16 one by one, and the rotating disk 5 is provided with 9 oil guide channels 19 inside, and the openings of one end of the oil guide channels 19 are connected to the ball sockets 16 one by one, and the openings of the other end of the oil guide channels 19 are connected to the waist-shaped grooves 17 one by one.

[0043] like Figure 6 As shown, the edge of the assembly surface of the floating swash plate 6 is provided with an annular outer auxiliary support belt 14, and the assembly surface of the floating swash plate 6 is provided with an inner auxiliary support belt 15 around the central through hole, thereby forming a concentric double ring distribution of the outer auxiliary support belt 14 and the inner auxiliary support belt 15. The assembly surface of the floating swash plate 6 is provided with a sealing belt 13 between the outer auxiliary support belt 14 and the inner auxiliary support belt 15. When the assembly surface of the rotating plate 5 is rotated and assembled to the assembly surface of the floating swash plate 6, the sealing belt 13 presses each waist groove 17 of the assembly surface of the rotating plate 5, thereby each waist groove 17 forms a static pressure oil chamber through the sealing belt 13.

[0044] As a further improvement of the present invention, in this embodiment, a gasket can also be installed on the assembly surface of the floating swash plate 6, and the gasket replaces the assembly surface of the floating swash plate 6 facing the assembly surface of the turntable 5, and the outer auxiliary support belt 14, the inner auxiliary support belt 15, and the sealing belt 13 are all arranged on the side of the gasket facing the turntable 5.

[0045] like Figure 7 , Figure 8 , Fig. 9 , Fig.10 As shown, in this embodiment, a ball joint 20 is slidably installed through a boss in the cylinder body 3 toward the middle of the front end of the turntable 5, and the front end of the ball joint 20 is hinged to the central through hole of the turntable 5. A plurality of spring holes 25 are provided in the cylinder body 3, and the spring holes 25 are circumferentially distributed around the central through hole of the cylinder body 3 at equal intervals. A spring 8 is installed in each spring hole 25, and the front end of each spring 8 passes through the front end of the spring hole 25 and then presses against the ball joint 20, and the rear end of each spring 8 contacts the rear end wall of the spring hole 25.

[0046] There are 9 plunger cavities 21 in the cylinder body 3. The front end of each plunger cavity 21 is located at the front end of the cylinder body 3 to form a cavity opening. The rear end of each plunger cavity 21 is opened at the rear end of the cylinder body 3 to form an oil port. The oil port is used for hydraulic oil to enter the plunger cavity 21 and for the hydraulic oil pressed out of the plunger cavity 21 to flow out. The distribution plate 2 is coaxially installed at the rear end of the cylinder body 3. The distribution plate 2 has a distribution hole, which is used to connect the oil port at the rear end of the plunger cavity 21.

[0047] The nine plunger cavities 12 are circumferentially distributed around the central through hole of the cylinder body 3 at equal intervals, and the nine conical plungers 4 are installed in the plunger cavities 21 one by one. The front end of each conical plunger 4 passes through the front end of the corresponding plunger cavity 21 as a ball head end, and the ball heads of the nine conical plungers 4 are correspondingly ball-jointed in the ball sockets 16 of the ball joint mounting surface of the rotary disk 5, and the rear end of each conical plunger 4 is located in the plunger cavity 21. Fig.11 As shown, each conical plunger 4 has a central through hole, the rear end of the central through hole of each conical plunger 4 is connected to the plunger cavity 21, and the front end of the central through hole of each conical plunger 4 is connected to the ball socket 16 in the rotary disk 5.

[0048] like Fig.12 As shown, a circular groove 23 is provided on the circumferential outer surface of the rear end of each tapered plunger 4 , and the circular groove 23 is used to install the metal sealing ring 7 to achieve sealing between the tapered plunger 4 and the corresponding plunger cavity 21 .

[0049] The main shaft 1 passes through the central through hole of the valve plate 2, the cylinder body 3, the rotary plate 5, the floating swash plate 6, the base 9, the bearing 10, and the flange 12 in sequence. And only in the central through hole of the cylinder body 3 is a spline formed to cooperate with the spline at the corresponding position of the main shaft 1, so that only the cylinder body 3 is fixedly connected to the main shaft 1 among the above components. Therefore, when the main shaft 1 rotates, the cylinder body 3 and each tapered plunger 4 are driven to rotate as a whole, and the rotary plate 5 is driven to rotate through the tapered plunger 4.

[0050] In this embodiment, the material of the rotating plate 5 and the material of the floating swash plate 6 are tribologically compatible. When used in a light-load pump, the floating swash plate 6 is made of steel, and the rotating plate 5 is made of all copper. When used in a heavy-load pump, the floating swash plate 6 is made of steel, and the rotating plate 5 uses carbon steel as the base material, and the assembly surface of the rotating plate 5 is a bimetallic composite material formed by molten cast or sintered copper alloy. If the rotating plate 5 is made of all steel, the floating swash plate 6 uses steel as the base material, and the assembly surface of the floating swash plate 6 is a molten copper bimetallic material.

[0051] In this embodiment, there is a static pressure oil chamber formed by a sealing belt 13, a waist-shaped groove 17, etc. between the rotating plate 5 and the floating inclined plate 6. When hydraulic oil is introduced into the static pressure oil chamber, a static pressure support can be formed. The ball head end of the tapered plunger 4 is hinged in the ball socket 16 of the rotating plate 5, and the tail of the tapered plunger 4 cooperates with the plunger cavity 21 in the cylinder body 3.

[0052] This embodiment is applied to a swash plate type axial piston pump, and the floating swash plate 6 can be used to replace the original swash plate. An oil guide channel 19 is provided in the rotating plate 5, and a process hole processed with a seal is used. The hydraulic oil from the plunger cavity 21 enters the ball socket 16 of the rotating plate 5 through the central through hole of the tapered plunger 4, and then flows to the waist-shaped groove 17 of the rotating plate 5 through the oil guide channel 19, and then enters the static pressure oil chamber formed by the sealing belt 13 on the assembly surface of the floating swash plate 6 and the waist-shaped groove 17 on the assembly surface of the rotating plate. The waist-shaped groove 17 on the assembly surface of the rotating plate 5 cooperates with the sealing belt 13 on the assembly surface of the floating swash plate 6. When the rotating plate 5 and the floating swash plate 6 slide relative to each other, the sealing belt 13 will form an oil film as a static pressure support. At this time, the static pressure support between the rotating plate 5 and the floating swash plate 6 will balance the force of the tapered plunger 4 on the rotating plate 5. The outer auxiliary support belt 14 and the inner auxiliary support belt 15 provided on the assembly surface of the floating swash plate 6 can balance the residual pressing force and ensure sufficient oil film lubrication.

[0053] In this embodiment, a spring 8 is arranged in the spring hole 25 in the cylinder body 3. The spring 8 is a compression spring. One end of the spring 8 acts on the cylinder body 3, and the other end acts on the ball joint 20. When the pump oil pressure has not been established, the spring 8 provides a return force for the tapered plunger 4 on the one hand, and pushes the cylinder body 3 to press against the distribution plate 2 and the rotating plate 5 on the other hand, so that the rotating plate 5 is pressed tightly against the surface of the floating swash plate 6, thereby ensuring the initial pre-sealing performance of the distribution pair and the rotating plate pair.

[0054] like Fig.11 , Fig.12 , Fig.13 , Fig.14 As shown, in this embodiment, the mouth of each ball socket 16 on the ball joint mounting surface of the rotary disk 5 is formed into a cylindrical mouth 18, and the outer circumferential surface of the ball head end of the tapered plunger 4 is provided with an annular groove 22, and the central axis of the annular groove 22 forms an angle (not 0°, not 180°) with the central axis of the tapered plunger 4. Suppose the diameter of the annular groove 22 is recorded as D 1, the diameter of the cylindrical opening 18 is recorded as D 2. In this embodiment, the diameter of the annular groove 22 at the ball end of the tapered plunger 4 is D 1 is smaller than the diameter of the cylindrical opening 18 of the ball socket 16 D2, thus, when the ball head of the tapered plunger 4 is assembled in the ball socket 16, a size matching relationship can be formed, and the effect that can be achieved is: when the annular groove 22 of the ball head end of the tapered plunger 4 maintains a parallel relationship with the cylindrical opening 18 of the ball socket 16, that is, a coaxial relationship, the ball head end of the tapered plunger 4 can be inserted into the ball socket 16 of the rotating disk 5; after the ball head end of the tapered plunger 4 enters the ball socket 16 of the rotating disk 5, if the parallel geometric relationship between the annular groove 22 of the ball head end of the tapered plunger 4 and the cylindrical opening 18 of the ball socket 16 is changed, that is, the coaxial geometric relationship is not present, the ball head end of the tapered plunger 4 is hinged in the ball socket 16 of the rotating disk 5. Therefore, during the operation of the plunger pump, even when the inclination angle of the floating swash plate 6 is 0°, the ball head end of the tapered plunger 4 can maintain an articulated relationship with the ball socket 16 of the rotating disk 5 and will not fall off.

[0055] In this embodiment, the inclination angle of the floating swash plate 6 relative to the base 9 can be adjusted, thereby achieving stepless regulation of the flow rate.

[0056] The working process of this embodiment is as follows:

[0057] The conical plunger 4 is installed in the cylinder hole of the cylinder body 3, the ball head end of the conical plunger 4 is hinged to the ball socket 16 of the rotating plate 5, the floating swash plate 6 is installed on the base 9, the base 9 is axially fixed by the bearing 10, and the rotating plate 5 is assembled on the floating swash plate 6 through a static pressure support. Driven by the prime mover, the main shaft 1 drives the cylinder body 3 and the tapered plunger 4 in the cylinder body 3 to move through the spline connection. When the cylinder body 3 and the turntable 5 rotate, the tapered plunger 4 gradually extends outward within the half circle (0~π) of rotation from bottom to top in the cylinder body 3, so that the volume of the sealed working chamber of the plunger chamber 21 of the cylinder body 3 continues to increase, generating a local vacuum, and the hydraulic oil is sucked in through the distribution holes on the distribution plate 2; on the contrary, when the tapered plunger 4 gradually retracts into the cylinder body 3 within the half circle (π~2π) of its rotation from top to bottom, the volume of the sealed working chamber of the plunger chamber 21 continues to decrease, that is, the oil is pressed out through the rear end oil port of the plunger chamber 21 and the distribution holes on the distribution plate 2.

[0058] Each time the cylinder body 3 rotates one circle, each conical plunger 4 reciprocates once, completing one oil suction and oil compression. The hydraulic oil in the plunger cavity 21 enters the waist groove 17 of the rotating disk 5 through the oil guide channel 19 at the ball socket 16 of the rotating disk 5. The waist groove 17 cooperates with the sealing belt 13 of the floating swash plate 6. When the floating swash plate 6 and the rotating disk 5 slide relative to each other, an oil film will be formed at the sealing belt 13. At this time, the static pressure support force formed between the rotating disk 5 and the floating swash plate 6 will balance the force of the conical plunger 4 on the rotating disk 5. The surface of the floating swash plate 6 is provided with inner and outer auxiliary support belts 14 and 15 to balance the residual pressure, which can ensure that the lubricating oil is fully lubricated. The inclination angle of the floating swash plate 6 relative to the base 9 can be adjusted, thereby realizing stepless adjustment of the flow rate.

[0059] The embodiments described in the present invention are merely descriptions of the preferred implementation modes of the present invention, and are not intended to limit the concept and scope of the present invention. Without departing from the design concept of the present invention, various modifications and improvements made to the technical solutions of the present invention by those skilled in the art should all fall within the protection scope of the present invention. The technical contents for which protection is sought in the present invention have all been recorded in the claims.

Claims

1. A floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate, comprising a cylinder body (3), a rotary plate (5), a floating swash plate (6), a base (9), a main shaft (1), and a plurality of conical plungers (4), wherein one side of the rotary plate (5) is rotatably mounted on one side of the floating swash plate (6), and the opposite sides of the rotary plate (5) and the floating swash plate (6) serve as respective assembly surfaces, the other side of the rotary plate (5) faces the cylinder body (3), and the other side of the rotary plate (5) serves as a ball joint mounting surface, the ball joint mounting surface of the rotary plate (5) is provided with a plurality of ball sockets (16), the cylinder body (3) is provided with a plurality of plunger cavities (21), and the conical plungers (4) are mounted in the plunger cavities one by one in a one-to-one correspondence. (21), the ball head end of each conical plunger (4) respectively extends from the plunger cavity (21) thereof toward one end of the rotary disk (5), and the ball heads of each conical plunger (4) are correspondingly ball-jointed in the ball socket (16) of the ball joint mounting surface of the rotary disk (5), and the other end of each plunger cavity (21) is used for passing hydraulic oil into or out of the hydraulic oil, the main shaft (1) sequentially passes through the cylinder body (3), the rotary disk (5), the floating swash plate (6), and the base (9), and the main shaft (1) is only fixedly connected to the cylinder body (3), and when the main shaft (1) rotates, it drives the cylinder body (3) and each conical plunger (4) to rotate as a whole, and drives the rotary disk (5) to rotate through the conical plunger (4), characterized in that The mouth of each ball socket (16) of the ball joint mounting surface of the rotary disk (5) is formed as a cylindrical mouth (18), and the circumferential outer surface of the ball head end of the tapered plunger (4) is formed with an annular groove (22), the central axis of the annular groove (22) is inclined at a certain angle compared to the central axis of the tapered plunger (4), the diameter of the annular groove (22) is smaller than the diameter of the cylindrical mouth (18), and when the ball head end of the tapered plunger (4) is ball-jointed in the ball socket (16), the annular groove (22) and the cylindrical mouth (18) form a size match; The assembly surface of the rotating disk (5) is provided with a plurality of grooves (17), and the rotating disk (5) is provided with a plurality of oil guide channels (19), the positions of the grooves (17) and the oil guide channels (19) all correspond to the ball sockets (16), and the openings at one end of the oil guide channels (19) are connected to the ball sockets (16) at the corresponding positions, and the openings at the other end of the oil guide channels (19) are connected to the grooves (17) at the corresponding positions, and the assembly surface of the floating swash plate (6) is provided with an outer auxiliary support belt (14) and an inner auxiliary support belt (15) distributed in a double ring, and a sealing belt (13) is provided on the assembly surface of the floating swash plate (6) between the outer auxiliary support belt (14) and the inner auxiliary support belt (15), and the sealing belt (13) is pressed onto each groove (17) on the assembly surface of the rotating disk (5), and the sealing belt (13) cooperates with each groove (17) to form a static pressure oil chamber respectively; The conical plunger (4) has a central through hole (24), one end of which is connected to a corresponding plunger cavity (21), and the other end of which is connected to a ball socket (16) at a corresponding position on the ball joint mounting surface of the rotary plate (5). The hydraulic oil in the plunger cavity (21) is introduced into the static pressure oil chamber through the central through hole (24) to form a static pressure support between the rotary plate (5) and the floating swash plate (6). Under the joint action of the sealing belt on the surface of the floating swash plate, the inner and outer auxiliary support belts and the rotary plate groove, the rotary plate is completely statically supported, so as to balance the force exerted by the plunger on the rotary plate.

2. A floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate according to claim 1, characterized in that: A ball joint (20) is movably mounted on one side of the cylinder body (3) facing the rotary disk (5). The ball joint (20) is hinged to a through hole of the rotary disk (5) through which the main shaft (1) passes. A plurality of spring holes (25) are also provided in the cylinder body (3). A spring (8) is respectively mounted in each spring hole (25). One end of each spring (8) passes through the spring hole (25) toward one end of the ball joint (20) and then presses against the ball joint (20).

3. The floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate according to claim 1, characterized in that: The material of the rotary plate (5) and the material of the floating swash plate (6) are tribologically compatible.

4. A floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate according to claim 3, characterized in that: When the floating swash plate (6) is made of steel, the rotating plate (5) is made of pure copper.

5. The floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate according to claim 3, characterized in that: When the floating swash plate (6) is made of steel, the rotating plate (5) uses carbon steel as a base material, and the assembly surface of the rotating plate (5) is a bimetallic composite material formed by a cast or sintered copper alloy.

6. The floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate according to claim 3, characterized in that: When the rotary plate (5) is made of all-steel material, the floating swash plate (6) uses steel material as a base material, and the assembly surface of the floating swash plate (6) is made of a molten copper bimetallic material.

7. The floating swash plate type conical plunger variable displacement pump rotating assembly without a pressure plate according to claim 1, characterized in that: A gasket is installed on the assembly surface of the floating swash plate (6), and the gasket replaces the assembly surface of the floating swash plate (6) facing the assembly surface of the rotating plate (5), and the outer auxiliary support belt (14), the inner auxiliary support belt (15), and the sealing belt (13) are all arranged on the side of the gasket facing the rotating plate (5).

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