CN111396279B - Force balance type two-dimensional plunger pump - Google Patents
Force balance type two-dimensional plunger pump Download PDFInfo
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- CN111396279B CN111396279B CN201811533199.9A CN201811533199A CN111396279B CN 111396279 B CN111396279 B CN 111396279B CN 201811533199 A CN201811533199 A CN 201811533199A CN 111396279 B CN111396279 B CN 111396279B
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- guide rail
- piston
- assembly
- pump core
- pump
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- 230000008878 coupling Effects 0.000 claims abstract description 35
- 238000010168 coupling process Methods 0.000 claims abstract description 35
- 238000005859 coupling reaction Methods 0.000 claims abstract description 35
- 230000005540 biological transmission Effects 0.000 claims abstract description 32
- 230000033001 locomotion Effects 0.000 claims description 25
- 230000001133 acceleration Effects 0.000 claims description 23
- 239000008358 core component Substances 0.000 claims description 17
- 239000000306 component Substances 0.000 claims description 16
- 238000007789 sealing Methods 0.000 claims description 13
- 238000009434 installation Methods 0.000 claims description 9
- 230000001360 synchronised effect Effects 0.000 claims description 4
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 230000000712 assembly Effects 0.000 abstract description 5
- 238000000429 assembly Methods 0.000 abstract description 5
- 239000003921 oil Substances 0.000 description 89
- 230000009471 action Effects 0.000 description 12
- 238000004891 communication Methods 0.000 description 11
- 238000005086 pumping Methods 0.000 description 10
- 239000007788 liquid Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 239000010720 hydraulic oil Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000007599 discharging Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/001—Noise damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/18—Lubricating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The force balance type two-dimensional piston pump comprises a front end cover, an upper coupler assembly, an upper coupling pump core assembly, a pump shell, an intermediate coupler assembly, a lower coupling pump core assembly and a rear end cover which are sequentially and coaxially arranged along an axial lead; the pump core body in the upper and lower pump core assemblies comprises a left guide rail assembly, a right guide rail assembly and a pump core assembly, wherein the left guide rail assembly and the right guide rail assembly respectively comprise a guide rail and a balance guide rail; the pump core assembly comprises a pump core cylinder body assembly and a piston assembly; the piston assembly comprises a transmission shaft, a left piston ring, a right piston ring and a piston; a right piston ring in the pump core body, a piston and a pump core cylinder body are enclosed to form a right closed cavity; the left piston ring, the piston and the pump core cylinder body enclose a left closed cavity; the right closed cavity is communicated with the first distributing groove of the piston, and the left closed cavity is communicated with the second distributing groove of the piston; the mass sum of the balance rotor formed by the left balance guide rail, the right balance guide rail, the transmission shaft, the left piston ring and the right piston ring is equal to the mass sum of the rotor formed by the left guide rail, the right guide rail and the piston.
Description
Technical Field
The invention relates to a hydraulic plunger pump, which belongs to a hydraulic pump and a hydraulic motor in the field of fluid transmission and control.
Background
The hydraulic pump is used as an energy power element in a hydraulic system and plays a decisive role in system performance and working efficiency. With the rapid development of industrial technology in China, the hydraulic pump is widely applied to important fields such as aerospace, marine ships and the like. However, the conventional plunger pump is difficult to achieve the aims of high efficiency, high pressure, light weight and small vibration due to the limitations of friction pairs, sizes and the like.
The traditional common axial plunger pump has more parts which move relatively in the axial plunger pump, has high requirements on material quality and processing precision, is sensitive to oil pollution, has higher requirements and cost for processing, using and maintaining, and has high price; the cylinder body rotates along with the transmission shaft, and the moment of inertia is large, so that the response speed of starting, stopping and speed regulation is slow, and the output flow of the pump is not controlled by speed regulation; the friction pairs in the cylinder body are more, the temperature rise of the cylinder body is quicker under high-speed rotation, and the abrasion of parts such as a valve plate, a plunger and the like directly affects the service life and the durability of the pump. Besides, due to the limitation of the working principle of the plunger pump, the transmission shaft rotates for one circle, each plunger can only realize one oil suction and one oil discharge, and the displacement of the plunger pump is limited.
Because of various drawbacks of the conventional plunger pump, patent document CN205895515U proposes a hydraulic pump of a novel structure, which can realize the oil sucking and discharging function by axially moving while rotating by using the motion principle of two degrees of freedom of the piston, and is named as a two-dimensional 2D piston pump because of the motion in two dimensions during operation. The double-freedom-degree motion principle is applied to the design of a piston of a pump, and a novel flow distribution mode is formed.
Patent document CN105484962 proposes a two-dimensional 2D duplex axial piston pump, which adopts a common rail transmission mode, and realizes the reciprocation and rotation of a two-dimensional 2D piston. Compared with the traditional hydraulic pump, the two-dimensional 2D duplex piston pump has the advantages of novel and compact structure, no flow pulsation, small volume, light weight, simple transmission, easy speed regulation, high discharge and high volumetric efficiency. However, the two-dimensional 2D duplex piston pump has the disadvantages of high speed, running stability, heavy load and the like.
Disclosure of Invention
In order to overcome the defects of the conventional two-dimensional 2D piston pump, the invention provides a force balance type two-dimensional 2D axial piston pump which can realize continuous oil suction and discharge functions by utilizing the two degrees of freedom of a piston and simultaneously axially moving the piston.
The technical implementation scheme of the invention is as follows:
the force balance type two-dimensional piston pump comprises a front end cover, an upper coupler assembly, an upper coupling pump core assembly, a pump shell, an intermediate coupler assembly, a lower coupling pump core assembly and a rear end cover which are sequentially and coaxially arranged along an axial lead. The left side and the right side of the inner wall of the pump shell are respectively provided with an annular groove, the annular grooves on the two sides are communicated with each other through a long straight oil duct, and the long straight oil duct is communicated with an oil outlet of the pump shell. The pump shell oil inlet and the pump shell oil outlet are respectively positioned at the opposite sides of the pump shell.
The inner cavity of the pump shell is formed by enclosing the pump shell, an upper pump core component at the left end of the pump shell and a lower pump core component at the right end of the pump shell.
The upper pump core component and the lower pump core component respectively comprise a pump core body arranged in the pump shell, and the pump core body of the upper pump core component and the pump core body of the lower pump core component are respectively arranged at the left end and the right end of the pump shell and are axially opposite in installation direction. The pump core body comprises a left guide rail assembly, a right guide rail assembly and a pump core assembly. The left guide rail component and the right guide rail component are symmetrically arranged at two ends of the pump core component.
The pumping cartridge assembly includes a pumping cartridge cylinder assembly and a piston assembly.
The pump core cylinder assembly comprises a pair of low-pressure columns arranged along a first diameter of the pump core cylinder and a pair of high-pressure columns arranged along a second diameter of the pump core cylinder, wherein the first diameter and the second diameter are mutually perpendicular and are positioned at different positions of an axial lead. The low-pressure column is provided with a U-shaped groove at one end close to the axis, and the high-pressure column is provided with a through inner hole. The low-pressure column and the high-pressure column are respectively connected with a cone roller through bearings; the pump core cylinder body comprises an outer ring and an inner ring which are concentrically arranged, a pair of oil outlet holes and a pair of oil inlet holes are formed in the inner ring, the oil outlet holes and the oil inlet holes are rectangular holes which are uniformly distributed at intervals in the circumferential direction, the oil inlet holes are communicated with a U-shaped groove of the low-pressure column, and the oil outlet holes are communicated with an inner hole of the high-pressure column; the outer ring is provided with a high-pressure column and a low-pressure column mounting hole, wherein the high-pressure column mounting hole is communicated with an annular groove on the inner wall of the pump shell.
The piston assembly is arranged in the inner ring in a penetrating manner along the axial lead direction and comprises a transmission shaft, a left piston ring, a right piston ring and a piston. The two sides of the piston are provided with step wall surfaces, the piston wall surfaces are provided with a pair of first distributing grooves and a pair of second distributing grooves, the first distributing grooves and the second distributing grooves are alternately and uniformly distributed, the first distributing grooves and the second distributing grooves are U-shaped distributing grooves with opposite axial openings, and the width of the U-shaped distributing grooves is consistent with the width of rectangular holes on the inner ring. The left piston ring and the right piston ring are respectively sleeved on steps at two sides of the piston, and the installation directions are axially opposite. The outer circle of the transmission shaft is in clearance fit with the inner circle of the piston, and the transmission shaft and the piston axially move relatively.
The left guide rail assembly comprises a left guide rail and a left balance guide rail, and the right guide rail assembly comprises a right guide rail and a right balance guide rail. The left guide rail component and the right guide rail component are identical in structure and axially reverse. The side close to the pump core cylinder body assembly is taken as the inner side, the track surfaces of the right guide rail, the right balance guide rail, the left guide rail and the left balance guide rail are all arranged inwards, the conical roller connected to the high-pressure column rolls on the right guide rail and the right balance guide rail, and the conical roller connected to the low-pressure column rolls on the left guide rail and the left balance guide rail. The left guide rail and the right guide rail are respectively fixed at two ends of the piston. The left balance guide rail is connected with the left piston ring, the right balance guide rail is connected with the right piston ring, and the left balance guide rail and the right balance guide rail are respectively fixed at two ends of the transmission shaft. The phases of the equal acceleration and equal deceleration curved surfaces of the left balance guide rail and the right balance guide rail are consistent, namely 2 highest points of the equal acceleration and equal deceleration curved surfaces of the left balance guide rail and the right balance guide rail correspond to 2 lowest points. The phases of the equal acceleration and deceleration curved surfaces of the left guide rail and the right guide rail are consistent, namely 2 highest points of the equal acceleration and deceleration curved surfaces of the left guide rail and the right guide rail correspond to 2 lowest points. The phases of the equal acceleration and equal deceleration curved surfaces of the left balance guide rail and the left guide rail are staggered by 90 degrees in the circumferential direction, namely, the lowest point of the equal acceleration and equal deceleration curved surface of the left balance guide rail corresponds to the highest point of the equal acceleration and equal deceleration curved surface of the left guide rail. The equal acceleration and equal deceleration curved surfaces of the right balance guide rail and the right guide rail are circumferentially staggered by 90 degrees, namely, the lowest point of the equal acceleration and equal deceleration curved surface of the right balance guide rail corresponds to the highest point of the equal acceleration and equal deceleration curved surface of the right guide rail.
And the right piston ring in the pump core body, the piston and the pump core cylinder body enclose a right closed cavity. And the outer circle on the inner side of the right piston ring is flush with the outermost circle in the middle of the piston, and is in clearance fit with the inner circle of the pump core cylinder, and the inner circle on the inner side of the right piston ring is in clearance fit with the outer circle of the right step of the piston. The left piston ring in the pump core body, the piston and the pump core cylinder body enclose a left closed cavity, and the sealing mode of each part is consistent with that of the right closed cavity. The right closed cavity is always communicated with the first distributing groove of the piston, and the left closed cavity is always communicated with the second distributing groove of the piston.
The mass sum of the balance rotor formed by the left balance guide rail, the right balance guide rail, the transmission shaft, the left piston ring and the right piston ring is equal to the mass sum of the rotor formed by the left guide rail, the right guide rail and the piston.
The middle coupler assembly is respectively connected with a right guide rail assembly in the upper pump core assembly and a guide rail assembly with the same name in the lower pump core assembly through a shifting fork structure, so that the middle coupler assembly and the right guide rail assembly can synchronously rotate in the circumferential direction and can axially and relatively slide. All parts of the upper pump core assembly and the parts with the same name in the lower pump core assembly are in a circumferential phase difference of 45 degrees.
The left end of the upper coupling component is axially fixed with the front end cover through a bearing and a sealing ring, the right end of the upper coupling component is connected with a left guide rail component in the upper coupling pump core component through a shifting fork structure, and the upper coupling component and the left guide rail component of the upper coupling pump core component realize free relative axial movement while keeping synchronous rotation.
The force balance type two-dimensional piston pump is characterized in that oil enters the inner cavity of the pump shell from the oil inlet below the pump shell. The left end of the cavity is sealed by the upper pump core component and the pump shell through a sealing piece, and the right end of the cavity is sealed by the lower pump core component and the pump shell through a sealing piece. The oil in the cavity flows through the U-shaped groove of the low-pressure column to the oil inlet of the pump core cylinder body.
When the pair of cone rollers fixed by the high-pressure column is contacted with the lowest point of the left guide rail curved surface and the highest point of the left balance guide rail curved surface, the pair of cone rollers fixed by the low-pressure column is contacted with the highest point of the right guide rail curved surface and the lowest point of the right balance guide rail. In the process of turning the left guide rail curved surface from the lowest point to the highest point, the piston is driven to rotate in the same direction and move leftwards, and the piston drives the right guide rail curved surface to turn from the highest point to the lowest point. In the process that the right balance guide rail turns from the lowest point to the highest point, the right piston ring and the transmission shaft are driven to rotate in the same direction and move rightward, the transmission shaft drives the left balance guide rail to turn from the highest point to the lowest point, and the left balance guide rail drives the left piston ring to rotate in the same direction and move rightward. The piston rotates circumferentially to enable the first distributing groove to be communicated with the oil inlet hole of the pump core cylinder body. The piston moves leftwards and the right piston ring moves rightwards so that the right sealing cavity is expanded, and oil is sucked into the right sealing cavity.
In the process of turning the curved surface of the left balance guide rail from the lowest point to the highest point, the left piston ring and the transmission shaft are driven to rotate in the same direction and move leftwards, the transmission shaft drives the right balance guide rail to turn from the highest point to the lowest point, and the right balance guide rail drives the right piston ring to rotate in the same direction and move leftwards. In the process of turning the curved surface of the right guide rail from the lowest point to the highest point, the piston is driven to rotate in the same direction and move rightward, and the piston drives the curved surface of the left guide rail to turn from the highest point to the lowest point. The piston rotates circumferentially to enable the first distributing groove to be communicated with the oil outlet hole of the pump core cylinder body. The piston moves rightwards and the right piston ring moves leftwards to enable the upper right sealing cavity to be compressed, and compressed high-pressure oil liquid enters an inner hole of the high-pressure column when being communicated with an oil outlet of the pump core cylinder body through the first distributing groove. The high-pressure oil in the inner hole of the high-pressure column flows through the long straight oil duct to flow out from the oil outlet above the pump shell after converging at the annular grooves on the left side and the right side of the pump shell.
The oil sucking and discharging mode of the left closed cavity is the same as that of the right closed cavity, but the phases are opposite.
Because the circumferential phase difference of 45 degrees exists between the upper pump core assembly and the lower pump core assembly, the pumping oil curves of the upper pump core assembly and the lower pump core assembly are reversed, and therefore fluctuation of the pumped oil quantity is partially counteracted, and the oil output is relatively balanced.
The mass sum of the balance rotor formed by the left balance guide rail, the right balance guide rail, the transmission shaft, the left piston ring and the right piston ring is equal to the mass sum of the rotor formed by the left guide rail, the right guide rail and the piston, and the regular axial reverse motion counteracts the inertia force generated by the axial reciprocating motion of the two rotors.
Further, the front end cover is fixedly connected to the left end face of the pump shell through bolts, and the rear end cover is fixedly connected to the right end face of the pump shell through bolts.
Further, the pump core body of the upper pump core assembly and the pump core body of the lower pump core assembly are arranged on two sides of the pump shell through threads, and the installation directions are axially opposite.
Under the connection of the intermediate coupling component, the equal-acceleration and equal-deceleration curved surface of the right guide rail component in the upper pump core component and the equal-acceleration and equal-deceleration curved surface of the right guide rail component in the lower pump core component are in a phase difference of 45 degrees, namely the highest point of the equal-acceleration and equal-deceleration curved surface of the right guide rail in the upper pump core component corresponds to the middle point of the equal-acceleration and equal-deceleration curved surface of the right guide rail in the lower pump core component.
The pump core body of the upper pump core assembly and the pump core body of the lower pump core assembly have the same structure, the installation directions are axially opposite, similarly, the left guide rail assembly and the right guide rail assembly in the pump core bodies have the same structure, the installation directions are axially opposite, and the corresponding parts in the two pump core bodies, the left guide rail assembly and the right guide rail assembly are called as homonymous parts. The axial direction of the pump is along the axial lead direction, and the axial lead of the pump is on the central axis of the pump shell.
Further, a left concentric ring is arranged between the left piston ring and the piston, and a right concentric ring is arranged between the right piston ring and the piston. The left side of the left concentric ring is provided with a left check ring, and the right side of the right concentric ring is provided with a right check ring.
Further, concentric rings are arranged between the inner ring of the pump core cylinder body and the left and right piston rings and the pistons, 2 pairs of rectangular holes which are uniformly distributed in the circumferential direction are respectively a low-pressure hole and a high-pressure hole, the outer circle of each concentric ring is in interference fit with the inner wall of the through hole of the pump core cylinder body, the oil inlet hole of the pump core cylinder body corresponds to the low-pressure hole of each concentric ring, and the oil outlet hole of the pump core cylinder body corresponds to the high-pressure hole of each concentric ring and is communicated with each other.
The beneficial effects of the invention are mainly shown in the following steps:
1. the volume change is completed by the cooperation of the piston and the piston ring, and compared with the volume change of a single piston, the volume change is doubled, and the space is saved. When the stroke and the displacement are unchanged, the cross section area is reduced, so that the stress of the guide rail and the conical roller is reduced, and high load is easy to realize.
2. The structure of the left piston ring, the right piston ring, the piston, the transmission shaft, the guide rail and the balance guide rail which are matched with each other is used for balancing the inertia force, so that the mechanical vibration during operation is reduced, the output rotating speed of the motor is more stable, and the flow pulsation is reduced. Meanwhile, the output torque of the motor can be reduced, and the energy is saved.
3. The transmission part is lubricated in oil, so that the mechanical efficiency is high and the abrasion is reduced.
Drawings
Fig. 1 is a schematic view of the assembly of the present invention.
Fig. 2 is a schematic view of the pump housing structure of the present invention.
Fig. 3 is a schematic diagram of the components within the pump of the present invention.
Fig. 4 is a schematic view of an upper pump core assembly of the present invention.
Fig. 5 a-5 b are schematic illustrations of a pump core cylinder assembly of the present invention. Wherein fig. 5a is a schematic view of a part of the pump core cylinder assembly of the present invention and fig. 5b is an exploded view of the pump core cylinder assembly of the present invention.
Fig. 6 a-6 c are views of a piston assembly of the present invention, with fig. 6c corresponding to the section line A-A of fig. 6 b. Wherein fig. 6a is a front view of the piston assembly of the present invention, fig. 6b is a top view of the piston assembly of the present invention, and fig. 6c is a cross-sectional view of the piston of the present invention.
Fig. 7 a-7 d are cross-sectional views of an upper pump core assembly and pump casing of the present invention. Wherein fig. 7a is a schematic diagram of an upper right closed cavity of the present invention, fig. 7b is a schematic diagram of an upper left closed cavity of the present invention, fig. 7c is a top cross-sectional view of an upper pump core assembly and a pump casing, and fig. 7d is a front cross-sectional view of an upper pump core assembly and a pump casing of the present invention.
Fig. 8a to 8b are assembly views of the upper left and right rail assemblies of the present invention. Wherein fig. 8a is an assembled front view of the upper left and right rail assemblies of the present invention, and fig. 8b is an assembled top view of the upper left and right rail assemblies of the present invention.
Fig. 9 a-9 b are views of the upper left rail of the present invention. Wherein fig. 9a is a front view of the upper left rail of the present invention, and fig. 9b is a left view of the upper left rail of the present invention.
Fig. 10a to 10c are three views of the upper left balance rail of the present invention. Wherein fig. 10a is a front view of the upper left balance rail of the present invention, fig. 10b is a left view of the upper left balance rail of the present invention, and fig. 10c is a top view of the upper left balance rail of the present invention.
FIG. 11 is a schematic view of an upper track assembly of the present invention.
Fig. 12 is a schematic view of an upper coupling assembly of the present invention.
Fig. 13 a-13 c are schematic views of an intermediate coupling assembly of the present invention. Wherein fig. 13a is an exploded view of the intermediate coupling assembly of the present invention, fig. 13b is a left side view of the intermediate coupling assembly of the present invention, and fig. 13c is a right side view of the intermediate coupling assembly of the present invention.
Fig. 14 is a schematic diagram of the present invention.
FIGS. 15 a-15 d are cross-sectional views of the flow channel of the present invention taken through 0-180, corresponding to the line A-A in FIG. 14. Wherein fig. 15a is a flow passage sectional view of the present invention turned to 0 ° 180 °, fig. 15b is a flow passage sectional view of the present invention turned to 45 °, fig. 15c is a flow passage sectional view of the present invention turned to 90 °, and fig. 15d is a flow passage sectional view of the present invention turned to 135 °.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
The force balance type two-dimensional piston pump comprises a front end cover 1, an upper coupler assembly 2, an upper pump core assembly 3, a pump shell 4, an intermediate coupler assembly 5, a lower pump core assembly 6 and a rear end cover 7 which are sequentially and coaxially arranged along an axial lead. The front end cover 1 is fixedly connected to the left end face of the pump shell 4 through bolts, and the rear end cover 7 is fixedly connected to the right end face of the pump shell 4 through bolts. The intermediate coupling assembly 5 is constrained by the upper pump core assembly 3 and the lower pump core assembly 6, whereby the intermediate coupling assembly 5 is axially fixed for rotation within the pump housing 4. The left end of the upper coupler assembly 2 is axially fixed with the front end cover 1 through a bearing and a sealing ring, the right end of the upper coupler assembly 2 is restrained by the upper coupling pump core assembly 3, and therefore the upper coupler assembly 2 is axially fixed and can circumferentially rotate in the pump shell 4.
The left side and the right side of the inside of the pump shell 4 are respectively provided with an annular groove, and the annular grooves comprise an annular groove 4A on the left side and an annular groove 4E on the right side. The left annular groove 4A and the right annular groove 4E are communicated by a long straight oil duct 4D, and the long straight oil duct 4D is communicated with an oil outlet 4B of the pump shell 4. The oil inlet 4C and the oil outlet 4B of the pump shell 4 are respectively positioned on the opposite sides of the pump shell. The left end of the inner cavity 4F of the pump shell 4 is sealed by the upper pump core assembly 3 and the pump shell 4 through a sealing piece, and the right end of the inner cavity 4F of the pump shell 4 is sealed by the lower pump core assembly 6 and the pump shell 4 through a sealing piece.
The upper pump core assembly 3 and the lower pump core assembly 6 respectively comprise a pump core body, and the pump core body of the upper pump core assembly 3 and the pump core body of the lower pump core assembly 6 are respectively fixed at the left end and the right end of the pump shell 4 through threads and have opposite installation directions. The pump core body comprises a left guide rail assembly 8, a right guide rail assembly 10 and a pump core assembly 9. The left guide rail assembly 8 and the right guide rail assembly 10 are symmetrically arranged at two ends of the pump core assembly 9.
The pump core assembly 9 comprises a pump core cylinder assembly 91 and a piston assembly 92.
The pumping block assembly 91 includes a pair of low pressure columns 912 disposed along a first diameter of the pumping block 915 and a pair of high pressure columns 914 disposed along a second diameter of the pumping block 915, the first diameter and the second diameter being perpendicular to each other and located at different locations along the axis. The end of the low-pressure column 912 near the axis is provided with a U-shaped groove 91A, and the high-pressure column 914 is provided with a through inner hole 91B. The low pressure column 912 is connected to a first tapered roller 911 via a bearing, and the high pressure column 914 is connected to a second tapered roller 913 via a bearing. The pump core cylinder 915 comprises an outer ring 91H and an inner ring 91E which are concentrically arranged, the inner ring 91E is provided with a pair of oil inlet holes 91F and a pair of oil outlet holes 91G, the oil outlet holes 91G and the oil inlet holes 91F are rectangular holes which are circumferentially and alternately distributed, the oil inlet holes 91F are communicated with a U-shaped groove 91A of the low-pressure column 912, and the oil outlet holes 91G are communicated with an inner hole 91B of the high-pressure column 914; the outer ring is provided with a mounting hole 91C of a high-pressure column 914 and a mounting hole 91D of a low-pressure column 912, wherein the mounting hole 91C of the high-pressure column in the upper pump core assembly 3 is communicated with the left annular groove 4A, and the mounting hole 91C of the high-pressure column in the lower pump core assembly 6 is communicated with the right annular groove 4E; the mounting hole 91C of the low pressure column communicates with the oil inlet hole 91F on the inner race. The left rail assembly 8 is in contact with only the second tapered roller 913 and the right rail assembly 10 is in contact with only the first tapered roller 911.
The piston assembly 92 is disposed in the inner ring 91E in a penetrating manner along the axial line direction, and includes a transmission shaft 921, a left piston ring 922, a right piston ring 929, a left retainer ring 923, a right retainer ring 927, a left concentric ring 924, a right concentric ring 926, a concentric ring 928, and a piston 925. 2 pairs of rectangular holes which are alternately and uniformly distributed in the circumferential direction are formed in the concentric ring 928, namely a low-pressure hole 92C and a high-pressure hole 92D, and the outer circle of the concentric ring 928 is in interference fit with the inner ring 91E of the pump core cylinder 915. The two ends of the piston 925 are provided with rectangular splines, a pair of first distributing grooves a and b and a pair of second distributing grooves C and D are circumferentially and alternately distributed on the wall surface of the piston 925, wherein the first distributing grooves a and b and the second distributing grooves C and D are U-shaped distributing grooves with opposite axial openings, and the widths of the first distributing grooves a and b and the second distributing grooves C and D are consistent with the widths of the high-pressure holes 92D and the low-pressure holes 92C of the concentric rings 928. The left and right concentric rings 924 and 926 are respectively fit over the first step 92B on either side of the piston 925. The left retainer ring 923 and the right retainer ring 927 are respectively sleeved on the two steps 92A at two sides of the piston 925 in an interference fit manner, so as to respectively fix the left concentric ring 924 and the right concentric ring 926. The primary step 92B is located between the piston 925 and the secondary step 92A. The side close to the pump core cylinder body is taken as the inner side, the outer side of the left piston ring 922 and the outer side of the right piston ring 929 are both U-shaped structures, the inner side is an annular structure, the U-shaped structure at the outer side of the left piston ring 922 is fixedly arranged on the left guide rail assembly 8 through a pin shaft, and the U-shaped structure at the outer side of the right piston ring 929 is fixedly arranged on the right guide rail assembly 10 through a pin shaft. The inner circle of the annular structure inside the left piston ring 922 is in clearance fit with the outer circle of the left concentric ring 924, the inner circle of the annular structure inside the right piston ring 929 is in clearance fit with the outer circle of the right concentric ring 926, and the left piston ring 922 and the right piston ring 929 are symmetrically arranged on two sides of the piston 925. The outer circle of the transmission shaft 921 is in clearance fit with the inner circle of the piston 925, and the transmission shaft 921 and the piston 925 axially move relatively. The transmission shaft 921 is respectively connected with the left balance guide rail 81 on the left guide rail assembly 8 and the right balance guide rail 102 on the right guide rail assembly 10 through rectangular keys at two ends, and the piston 925 is respectively connected with the left guide rail 82 on the left guide rail assembly 8 and the right guide rail 101 on the right guide rail assembly 10 through rectangular keys at two ends. The drive shaft 921 and the piston 925 reciprocate axially in opposite directions while simultaneously performing the same circumferential movement in the same direction under the constraint of the left rail assembly 8 and the right rail assembly 10.
The right piston ring 929, right concentric ring 926, piston 925 and concentric ring 928 in the pump core body enclose a right closed cavity B1. A gap seal is provided between the inner circumference of the concentric ring 928 and the outer circumference of the inner side of the right piston ring 929. A gap seal is provided between the inner circle of concentric ring 928 and the outer circle of piston 925. A gap seal is formed between the inner circle of the inner side of the right piston ring 929 and the outer circle of the right concentric ring 926. The left piston ring 922, the left concentric ring 924, the piston 925 and the concentric ring 928 in the pump core body enclose a left closed cavity A1, and the sealing mode of each component is consistent with that of the right closed cavity B1. The right closed cavity B1 is always in communication with the first distribution grooves a, B of the piston 925, and the left closed cavity A1 is always in communication with the second distribution grooves c, d of the piston 925. The low pressure holes 92C of the concentric ring 928 communicate with the oil inlet holes 91F of the pumping block 915, and the high pressure holes 92D of the concentric ring 928 communicate with the oil outlet holes 91G of the pumping block 915. The pistons 925 are constrained by the left and right rail assemblies 8, 10 to simultaneously rotate circumferentially and reciprocate axially within the concentric rings 928, which causes the pistons 925 to distribute fluid to and from the pumping core cylinder 915.
In the force balance type two-dimensional piston pump, oil enters into the cavity 4F inside the pump shell 4 from the oil inlet 4C below the pump shell 4. The oil in the containing chamber 4F flows through the U-shaped groove 91A of the low pressure column 912 to the oil inlet hole 91F of the pump core cylinder 915. The piston 925 simultaneously rotates circumferentially and reciprocates axially, and oil enters the right seal chamber B1 when the first distribution grooves a, B communicate with the low pressure holes 92C of the concentric ring 928. When the right seal cavity B1 is compressed, the oil in the right seal cavity B1 is pressurized to be high-pressure oil; at this time, the first distribution grooves a, B communicate with the high pressure holes 92D on the concentric ring 928, and the high pressure oil enters the inner hole 91B of the high pressure column 914. The high-pressure oil in the inner hole 91B of the high-pressure column 914 of the upper pump core assembly 3 flows through the long straight oil duct 4D after passing through the annular groove 4A on the left side of the pump shell 4, and flows out from the oil outlet 4B above the pump shell 4. The high-pressure oil in the inner hole 91B of the high-pressure column 914 of the lower pump core assembly 6 flows through the long straight oil duct 4D and flows out of the oil outlet 4B above the pump shell 4 after passing through the annular groove 4E on the right side of the pump shell 4. The left closed chamber A1 is pumped in the same way as the right closed chamber B1, but the pumping curves are in opposite phase.
The left rail assembly 8 includes a left rail 82 and a left balance rail 81, and the right rail assembly 10 includes a right rail 101 and a right balance rail 102. The left guide rail assembly 8 and the right guide rail assembly 10 have the same structure and are axially reversed. With the side close to the pump core cylinder assembly 91 as the inner side, the track surfaces of the right and right balance rails 101 and 102 and the left and left balance rails 82 and 81 are all disposed toward the inner side, the first tapered roller 911 rolls on the right and right balance rails 101 and 102, and the second tapered roller 913 rolls on the left and left balance rails 82 and 81.
The left guide rail 82 is in a circular shape, the inner side is a working surface which accords with a deceleration curve such as equal acceleration, the outer side is U-shaped, a rectangular key slot is formed in the center of the left guide rail 82, and the working surface of the left guide rail 82 is matched with the corresponding second cone roller 913 to rotate.
The left balance guide rail 81 is a circular ring, the inner side of the left balance guide rail 81 is a working surface which accords with a deceleration curve such as equal acceleration, the working surface is matched with a corresponding second cone roller 913 for rotation, 2 pairs of first slots 8B and second slots 8C which are alternately distributed are formed in the outer side of the left balance guide rail 81, the first slots 8C are used for installing the left guide rail 82, the second slots 8B and a pair of holes 8A formed in the two sides are used for connecting the left piston ring 922, and a rectangular key slot is formed in the center of the end face of the left balance guide rail 81. After the left guide rail 82 is installed in the first slot 8C of the left balance guide rail 81, 4 mounting grooves 8D are formed on the outer side of the left balance guide rail 81, and the mounting grooves 8D of the left guide rail assembly 8 of the upper pump core assembly 3 are used for mounting the upper coupler assembly 2; the middle coupling assembly 5 is mounted in the mounting groove 8D of the right rail assembly 10 of the upper pump core assembly 3 and the mounting groove 8D of the right rail assembly 10 of the lower pump core assembly 6.
The left rail 82 and the right rail 101 are fixed to both ends of the piston 925 by rectangular keys, respectively. The left balance guide rail 81 is fixedly connected with the left piston ring 922 through a pin, the right balance guide rail 102 is fixedly connected with the right piston ring 929 through a pin, and meanwhile, the left balance guide rail 81 and the right balance guide rail 102 are respectively fixed at two ends of the transmission shaft 921 through rectangular keys. The equal-acceleration and equal-deceleration curved surfaces of the left balance guide rail 81 and the right balance guide rail 102 are in phase correspondence, the equal-acceleration and equal-deceleration curved surfaces of the left guide rail 82 and the right guide rail 101 are in phase correspondence, and the equal-acceleration and equal-deceleration curved surfaces of the left balance guide rail 81 and the equal-acceleration and equal-deceleration curved surfaces of the left guide rail 82 are circumferentially offset by 90 degrees.
The left guide rail 82 performs circumferential movement, and under the constraint of the first conical roller 911 and the second conical roller 913, the left guide rail 82 and the right guide rail 101 drive the piston 925 to perform axial reciprocating movement while circumferentially rotating in the concentric ring 928; at the same time, the left balance rail 81 performs a circumferential rotation movement, and the left balance rail 81, the right balance rail 102, the transmission shaft 921, the left piston ring 922, and the right piston ring 929 perform an axial reciprocation movement while performing a circumferential synchronous rotation under the constraint of the first tapered roller 911 and the second tapered roller 913. The axial movement of the balance rotor composed of the left balance rail 81, the right balance rail 102, the transmission shaft 921, the left piston ring 922 and the right piston ring 929 is opposite to the axial movement of the rotor composed of the left rail 82, the right rail 101 and the piston 925. That is, in the axial direction, the left rail 82 and the right rail 101 are accelerated to move with respect to the curved surface, and the left balance rail 81 and the right balance rail 102 are accelerated to move with respect to the curved surface, and the axial directions of the two are opposite; the left guide rail 82 and the right guide rail 101 perform deceleration movements such as curved surfaces, the left balance guide rail 81 and the right balance guide rail 102 perform deceleration movements such as curved surfaces, and the axial movement directions of the left balance guide rail 81 and the right balance guide rail 102 are opposite; the mass sum of the balance rotor formed by the left balance guide rail 81, the right balance guide rail 102, the transmission shaft 921, the left piston ring 922 and the right piston ring 929 is equal to the mass sum of the rotor formed by the left guide rail 82, the right guide rail 101 and the piston 925, and the regular axial reverse motion counteracts the inertia force generated by the axial reciprocating motion of the two rotors.
The upper coupling assembly 2 comprises an upper coupling 21 and 4 first flat rollers 22. The side surface of the upper coupler 21 is circumferentially provided with 4 through holes 2C, the left end surface of the upper coupler 21 is provided with 2 pairs of through grooves 2A and 2B which are alternately distributed, and the right end surface of the upper coupler is hollowed out. The upper coupler 21 and the left guide rail assembly 8 of the upper pump core assembly 3 are connected with each other by adopting the following shifting fork structure: pins are placed at the 4 through holes 2C of the upper coupler 21 to fix the 4 first flat rollers 22, and the 4 first flat rollers 22 are placed in the mounting grooves 8D of the left rail assembly 8 of the upper pump core assembly 3. The upper coupling through grooves 2a,2b provide clearance for the left rail assembly 8 of the upper pump core assembly 3. So that the left rail assembly 8 of the upper pump core assembly 3 is free to move axially relative to each other while maintaining synchronous rotation.
The intermediate coupling assembly 5 comprises a stop collar 51, an intermediate coupling 52 and 8 second flat rollers 53. The limit sleeve 51 is a circular ring, and the inner circle of the limit sleeve is in interference fit with the outer circle of the intermediate coupling 52. The left side of the outer surface of the middle coupling 52 is provided with 4 left round holes 5B which are circumferentially distributed, the right side of the middle coupling is provided with 4 right round holes 5E which are circumferentially distributed, the left round holes 5B and the right round holes 5E are circumferentially arranged to form a phase difference of 45 degrees, the left end face is provided with 2 pairs of left end grooves 5A and 5C which are alternately distributed, and the right end face is provided with 2 pairs of right end grooves 5D and 5F which are alternately distributed.
The middle coupler 52 and the right guide rail assembly 10 of the upper pump core assembly 3 are connected with each other by adopting the following shifting fork structure: a pin is placed at the left circular hole 5B of the intermediate coupling 52 to fix 4 second flat rollers 53, and the 4 second flat rollers 53 are placed in the mounting groove 8D of the right rail assembly 10 of the upper pump core assembly 3. The intermediate coupling 52 is interconnected with the right rail assembly 10 of the lower pump core assembly 6 using the following fork structure: a pin is placed at the right circular hole 5E of the intermediate coupling 52 to fix 4 second flat rollers 53, and the 4 second flat rollers 53 are placed in the mounting groove 8D of the right rail assembly 10 of the tandem pump core assembly 6.
The left end grooves 5A,5C of the intermediate coupling 52 provide avoidance space for the axial movement of the right guide rail assembly 10 of the upper pump core assembly 3, and the right end grooves 5D,5F provide avoidance space for the axial movement of the right guide rail assembly 10 of the lower pump core assembly 6. Under the constraint of the intermediate coupling assembly 5, the equal-acceleration and equal-deceleration curved surface of the right guide rail assembly 10 of the upper pump core assembly 3 and the equal-acceleration and equal-deceleration curved surface of the right guide rail assembly 10 of the lower pump core assembly 6 are 45-degree phase differences.
Principle of operation
In the force balance type two-dimensional piston pump, oil enters into the cavity 4F inside the pump shell 4 from the oil inlet 4C below the pump shell 4. The oil in the containing chamber 4F flows through the U-shaped groove 91A of the low pressure column 912 to the oil inlet hole 91F of the pump core cylinder 915. The piston 925 rotates circumferentially such that the first distribution grooves a, B communicate with the low pressure holes 92C of the concentric ring 928 and oil enters the seal cavity B1. When the right seal chamber B1 is compressed, the oil in the right seal chamber B is pressurized to be high-pressure oil, and the first distribution grooves a, B communicate with the high-pressure holes 92D on the concentric ring 928, so that the high-pressure oil enters the inner hole 91B of the high-pressure column 914. The high-pressure oil in the inner hole 91B of the high-pressure column 914 of the upper pump core assembly 3 is converged at the annular groove 4A on the left side of the pump shell 4, and the high-pressure oil in the inner hole 91B of the high-pressure column 914 of the lower pump core assembly 6 is converged at the annular groove 4E on the right side of the pump shell 4, and then flows through the long straight oil duct 4D and flows out of the oil outlet 4B above the pump shell 4. The oil absorption and oil discharge of the left closed cavity A1 are consistent with those of the right closed cavity B1.
In fig. 7c, the moving parts of the hydraulic pump can be considered to be in a zero position, and the movement law is shown in fig. 15a to 15 d.
Initially, the circumferential rotation is 0 degrees, and the left piston ring 922, the right piston ring 929 and the piston 925 in the upper pump core assembly 3 move to the middle of the axial stroke. At this time, the volume of hydraulic oil contained in the right closed cavity B1 is equal to that of the hydraulic oil contained in the left closed cavity A1; the first distribution grooves a, b on the piston 925 are in communication with the low pressure holes 92C of the concentric ring 928, the second distribution grooves C, D on the piston 925 are in communication with the high pressure holes 92D of the concentric ring 928, and the openings are in a fully open state, i.e. the communication area is maximum. The left rail assembly 8 in the upper pump core assembly 3 is rotated clockwise as shown in fig. 14 under the influence of the upper coupling assembly 2. The right piston ring 929 moves rightward along the axial stroke under the action of the right balance guide rail 102, the piston 925 moves leftward along the axial stroke under the action of the left guide rail 82 and the right guide rail 101 so that the right closed cavity B1 becomes gradually larger, hydraulic oil flows in through the U-shaped groove 91A, and enters the right closed cavity B1 from the low pressure holes 92C of the concentric ring 928 through the first distribution grooves a, B. Simultaneously, under the action of the left balance guide rail 81, the left piston ring 922 moves rightward along the axial stroke, the piston 925 moves leftward to enable the left closed cavity A1 to be gradually reduced, and high-pressure oil flows out from the left closed cavity A1 through the second distribution grooves c and D, the high-pressure holes 92D of the concentric rings 928, the inner hole 91B, the annular groove 4A on the left side, the long straight oil duct 4D and the oil outlet 4B. The piston 925 performs axial reciprocation and simultaneously performs circumferential rotation under the action of the left rail 82 and the right rail 101, and its axial displacement conforms to a deceleration curve such as equal acceleration. As the piston 925 moves to the left along the axial stroke, it simultaneously rotates in the direction shown in fig. 15 a. The communication areas between the first distribution grooves a, b and the low pressure holes 92C of the concentric ring 928 and between the second distribution grooves C, D and the high pressure holes 92D of the concentric ring 928 become smaller gradually. The piston 925 of the upper pump core assembly 3 continues to move leftward along the axial stroke under the action of the left and right guide rails 82 and 101, and the left and right piston rings 922 and 929 continue to move rightward along the axial stroke under the action of the left and right balance guide rails 81 and 102, respectively.
After 45 degrees of rotation, the piston 925 of the upper pump core assembly 3 moves to the leftmost end of the axial stroke, the left piston ring 922 and the right piston ring 929 move to the rightmost end of the axial stroke, at this time, the volume of the right closed cavity B1 reaches the maximum, the volume of the left closed cavity A1 reaches the minimum, the communication areas between the first distributing grooves a, B of the piston 925 and the low pressure holes 92C of the concentric rings 928, and the communication areas between the second distributing grooves C, D and the high pressure holes 92D of the concentric rings 928 are completely closed, and the oil liquid contained in the left closed cavity A1 and the right closed cavity B1 is not communicated with the oil liquid contained in the containing cavity 4F and the inner hole 91B. The piston 925 of the upper pump core assembly 3 starts to move rightward along the axial stroke under the action of the left and right guide rails 82 and 101, and the left and right piston rings 922 and 929 start to move leftward along the axial stroke under the action of the left and right balance guide rails 81 and 102, respectively.
After 90 degrees of rotation, the left piston ring 922, the right piston ring 929 and the piston 925 of the upper pump core assembly 3 move to the middle position of the axial stroke, the volumes of the left closed cavity A1 and the right closed cavity B1 are equal, and the first distributing grooves a and B of the piston 925 are in a state of being completely opened, namely the communication area is maximum, with the high pressure holes 92D and the second distributing grooves C and D of the concentric ring 928 and the low pressure holes 92C of the concentric ring 928. Hydraulic oil flows in through the U-shaped groove 91A from the low pressure holes 92C of the concentric ring 928 through the second distribution grooves C, d into the left closed chamber A1. High-pressure oil flows out from the right closed cavity B1 through the first distributing grooves a and B, the high-pressure holes 92D of the concentric rings 928, the inner holes 91B, the annular grooves 4A on the left side, the long straight oil channels 4D and the oil outlets 4B. The piston 925 in the upper pump core assembly 3 continues to move rightward along the axial stroke under the action of the left and right guide rails 82 and 101, and the left and right piston rings 922 and 929 continue to move leftward along the axial stroke under the action of the left and right balance guide rails 81 and 102, respectively.
After 135 degrees of rotation, the piston 925 in the upper pump core part 3 moves to the rightmost end of the axial stroke, the left piston ring 922 and the right piston ring 929 move to the leftmost end of the axial stroke, the volume of the left closed cavity A1 reaches the maximum, the volume of the containing cavity B1 reaches the minimum, the communication areas between the first distributing grooves a, B of the piston 925 and the high pressure holes 92D of the concentric ring 928, and the communication areas between the second distributing grooves C, D and the low pressure holes 92C of the concentric ring 928 are completely closed, and the oil liquid contained in the left closed cavity A1 and the right closed cavity B1 is not communicated with the oil liquid contained in the containing cavity 4F and the inner hole 91B. The piston 925 in the upper pump core assembly 3 begins to move left along the axial stroke under the action of the left and right guide rails 82, 101, and the left and right piston rings 922, 929 begin to move right along the axial stroke under the action of the left and right balance guide rails 81, 102, respectively.
After 180 degrees of rotation, the positions and the movement trend of the moving parts in the force balance type two-dimensional piston pump are the same as those of the moment of fig. 15a, and the periodic movement is repeated from the next moment.
The working modes of the left closed cavity and the right closed cavity of the lower pump core assembly 6 are consistent with those of the left closed cavity A1 and the right closed cavity B1 of the upper pump core assembly 3, and the initial position is 45 degrees.
Any one of the pistons 925 is set to suck and drain oil 2 times each time the reciprocation is completed once every 360 degrees of rotation. The two pistons 925 perform reciprocating movement twice with 360 degrees of rotation, sucking and discharging oil 4 times each.
The embodiments described in the present specification are merely examples of implementation forms of the inventive concept, and the scope of protection of the present invention should not be construed as being limited to the specific forms set forth in the embodiments, and the scope of protection of the present invention and equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.
Claims (3)
1. The force balance type two-dimensional piston pump comprises a front end cover, an upper coupler assembly, an upper coupling pump core assembly, a pump shell, an intermediate coupler assembly, a lower coupling pump core assembly and a rear end cover which are sequentially and coaxially arranged along an axial lead; the left side and the right side of the inner wall of the pump shell are respectively provided with an annular groove, the annular grooves on the two sides are communicated with each other through a long straight oil duct, and the long straight oil duct is communicated with an oil outlet of the pump shell; the pump shell oil inlet and the pump shell oil outlet are respectively positioned at the opposite sides of the pump shell;
the inner cavity of the pump shell is formed by enclosing the pump shell with an upper pump core component at the left end of the pump shell and a lower pump core component at the right end of the pump shell;
the upper pump core assembly and the lower pump core assembly respectively comprise a pump core body arranged in the pump shell, and the pump core body of the upper pump core assembly and the pump core body of the lower pump core assembly are respectively arranged at the left end and the right end of the pump shell and have opposite installation directions; the pump core body comprises a left guide rail assembly, a right guide rail assembly and a pump core assembly; the left guide rail assembly and the right guide rail assembly are symmetrically arranged at two ends of the pump core assembly;
the pump core assembly comprises a pump core cylinder body assembly and a piston assembly;
the pump core cylinder body assembly comprises a pair of low-pressure columns arranged along a first diameter of the pump core cylinder body and a pair of high-pressure columns arranged along a second diameter of the pump core cylinder body, and the first diameter and the second diameter are mutually perpendicular and are positioned at different positions of an axial lead; the low-pressure column is provided with a U-shaped groove at one end close to the axis, and the high-pressure column is provided with a through inner hole; the low-pressure column and the high-pressure column are respectively connected with a cone roller through bearings; the pump core cylinder body comprises an outer ring and an inner ring which are concentrically arranged, a pair of oil outlet holes and a pair of oil inlet holes are formed in the inner ring, the oil outlet holes and the oil inlet holes are rectangular holes which are uniformly distributed at intervals in the circumferential direction, the oil inlet holes are communicated with a U-shaped groove of the low-pressure column, and the oil outlet holes are communicated with an inner hole of the high-pressure column; the outer ring is provided with a high-pressure column and a low-pressure column mounting hole, wherein the high-pressure column mounting hole is communicated with an annular groove on the inner wall of the pump shell;
the piston assembly is arranged in the inner ring in a penetrating manner along the axial lead direction and comprises a transmission shaft, a left piston ring, a right piston ring and a piston; the two sides of the piston are provided with step wall surfaces, the piston wall surfaces are provided with a pair of first distributing grooves and a pair of second distributing grooves, the first distributing grooves and the second distributing grooves are alternately and uniformly distributed, the first distributing grooves and the second distributing grooves are U-shaped distributing grooves with opposite axial openings, and the width of the U-shaped distributing grooves is consistent with the width of rectangular holes on the inner ring; the left piston ring and the right piston ring are respectively sleeved on steps at two sides of the piston, and the installation directions are axially opposite; the outer circle of the transmission shaft is in clearance fit with the inner circle of the piston, and the transmission shaft and the piston axially move relatively;
the left guide rail assembly comprises a left guide rail and a left balance guide rail, and the right guide rail assembly comprises a right guide rail and a right balance guide rail; the left guide rail component and the right guide rail component have the same structure and are axially reversed; the side close to the pump core cylinder body assembly is taken as the inner side, the track surfaces of the right guide rail, the right balance guide rail, the left guide rail and the left balance guide rail are all arranged inwards, the conical roller connected to the high-pressure column rolls on the right guide rail and the right balance guide rail, and the conical roller connected to the low-pressure column rolls on the left guide rail and the left balance guide rail; the left guide rail and the right guide rail are respectively fixed at two ends of the piston; the left balance guide rail is connected with the left piston ring, the right balance guide rail is connected with the right piston ring, and the left balance guide rail and the right balance guide rail are respectively fixed at two ends of the transmission shaft; the phases of equal acceleration and equal deceleration curved surfaces of the left balance guide rail and the right balance guide rail are consistent, namely 2 highest points and 2 lowest points of equal acceleration and equal deceleration curved surfaces of the left balance guide rail and the right balance guide rail are corresponding; the phases of the equal acceleration and equal deceleration curved surfaces of the left guide rail and the right guide rail are consistent, namely 2 highest points of the equal acceleration and equal deceleration curved surfaces of the left guide rail and the right guide rail correspond to 2 lowest points; the phases of the equal acceleration and equal deceleration curved surfaces of the left balance guide rail and the left guide rail are staggered by 90 degrees in the circumferential direction, namely, the lowest point of the equal acceleration and equal deceleration curved surface of the left balance guide rail corresponds to the highest point of the equal acceleration and equal deceleration curved surface of the left guide rail; the phases of the equal acceleration and equal deceleration curved surfaces of the right balance guide rail and the right guide rail are staggered by 90 degrees circumferentially, namely, the lowest point of the equal acceleration and equal deceleration curved surface of the right balance guide rail corresponds to the highest point of the equal acceleration and equal deceleration curved surface of the right guide rail;
the right piston ring in the pump core body, the piston and the pump core cylinder body enclose a right closed cavity; taking one side close to the pump core cylinder body as the inner side, enabling the outer circle on the inner side of the right piston ring to be flush with the outermost circle in the middle of the piston, enabling the outer circle on the inner side of the right piston ring to be in clearance fit with the inner circle of the pump core cylinder body, and enabling the inner circle on the inner side of the right piston ring to be in clearance fit with the outer circle of the right step of the piston; the left piston ring in the pump core body, the piston and the pump core cylinder body enclose a left closed cavity, and the sealing mode of each part is consistent with that of the right closed cavity; the right closed cavity is communicated with the first distributing groove of the piston all the time, and the left closed cavity is communicated with the second distributing groove of the piston all the time;
the mass sum of a balance rotor formed by the left balance guide rail, the right balance guide rail, the transmission shaft, the left piston ring and the right piston ring is equal to the mass sum of a rotor formed by the left guide rail, the right guide rail and the piston;
the middle coupler assembly is respectively connected with a right guide rail assembly in the upper pump core assembly and a guide rail assembly with the same name in the lower pump core assembly by a shifting fork structure, so that the middle coupler assembly and the right guide rail assembly can synchronously rotate in the circumferential direction and can axially and relatively slide; all parts of the upper pump core assembly and the parts with the same name in the lower pump core assembly have a circumferential phase difference of 45 degrees;
the left end of the upper coupler assembly is axially fixed with the front end cover through a bearing and a sealing ring, the right end of the upper coupler assembly is connected with a left guide rail assembly in the upper pump core assembly through a shifting fork structure, and the upper coupler assembly and the left guide rail assembly of the upper pump core assembly realize free relative axial movement while keeping synchronous rotation;
the front end cover is fixedly connected to the left end face of the pump shell through bolts, and the rear end cover is fixedly connected to the right end face of the pump shell through bolts;
the pump core body of the upper pump core assembly and the pump core body of the lower pump core assembly are arranged on two sides of the pump shell through threads, and the installation directions are axially opposite.
2. The force balanced two-dimensional piston pump as set forth in claim 1, wherein: a left concentric ring is arranged between the left piston ring and the piston, and a right concentric ring is arranged between the right piston ring and the piston; the left side of the left concentric ring is provided with a left check ring, and the right side of the right concentric ring is provided with a right check ring.
3. The force balanced two-dimensional piston pump as set forth in claim 1, wherein: the inner ring of the pump core cylinder body is provided with concentric rings, the left piston ring, the right piston ring and the piston, the concentric rings are provided with 2 pairs of rectangular holes uniformly distributed in the circumferential direction, namely a low-pressure hole and a high-pressure hole, the outer circle of each concentric ring is in interference fit with the inner wall of the through hole of the pump core cylinder body, the oil inlet hole of the pump core cylinder body corresponds to the low-pressure hole of the concentric ring, and the oil outlet hole of the pump core cylinder body corresponds to the high-pressure hole of the concentric ring and is communicated with each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811533199.9A CN111396279B (en) | 2018-12-14 | 2018-12-14 | Force balance type two-dimensional plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811533199.9A CN111396279B (en) | 2018-12-14 | 2018-12-14 | Force balance type two-dimensional plunger pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111396279A CN111396279A (en) | 2020-07-10 |
| CN111396279B true CN111396279B (en) | 2024-02-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811533199.9A Active CN111396279B (en) | 2018-12-14 | 2018-12-14 | Force balance type two-dimensional plunger pump |
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| CN112610438A (en) * | 2020-11-23 | 2021-04-06 | 河南航天液压气动技术有限公司 | Piston pump |
| CN114198277B (en) * | 2021-12-14 | 2023-03-31 | 浙江工业大学 | Gear drive reciprocating piston pump |
| CN114263584A (en) * | 2021-12-16 | 2022-04-01 | 北京空天技术研究所 | Tandem piston pump |
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| GB927005A (en) * | 1961-05-02 | 1963-05-22 | Budzich Tadeusz | Hydraulic pump or motor |
| GB9410011D0 (en) * | 1993-05-20 | 1994-07-06 | Willimczik Wolfhart | Rotary piston machines with a bearingless power train and stressless sliding parts |
| CN104791208A (en) * | 2015-04-01 | 2015-07-22 | 浙江工业大学 | Two-dimensional constant acceleration and deceleration guide rail axial piston pump |
| CN105484962A (en) * | 2015-12-18 | 2016-04-13 | 浙江工业大学 | Two-dimensional dual axial piston pump |
| CN205895515U (en) * | 2016-07-19 | 2017-01-18 | 浙江工业大学 | Two dimension awl gyro wheel piston pump |
| CN209838611U (en) * | 2018-12-14 | 2019-12-24 | 浙江工业大学 | Force balance two-dimensional plunger pump |
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Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB927005A (en) * | 1961-05-02 | 1963-05-22 | Budzich Tadeusz | Hydraulic pump or motor |
| GB9410011D0 (en) * | 1993-05-20 | 1994-07-06 | Willimczik Wolfhart | Rotary piston machines with a bearingless power train and stressless sliding parts |
| CN104791208A (en) * | 2015-04-01 | 2015-07-22 | 浙江工业大学 | Two-dimensional constant acceleration and deceleration guide rail axial piston pump |
| CN105484962A (en) * | 2015-12-18 | 2016-04-13 | 浙江工业大学 | Two-dimensional dual axial piston pump |
| CN205895515U (en) * | 2016-07-19 | 2017-01-18 | 浙江工业大学 | Two dimension awl gyro wheel piston pump |
| CN209838611U (en) * | 2018-12-14 | 2019-12-24 | 浙江工业大学 | Force balance two-dimensional plunger pump |
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