CN111396279A - Force balance type two-dimensional plunger pump - Google Patents
Force balance type two-dimensional plunger pump Download PDFInfo
- Publication number
- CN111396279A CN111396279A CN201811533199.9A CN201811533199A CN111396279A CN 111396279 A CN111396279 A CN 111396279A CN 201811533199 A CN201811533199 A CN 201811533199A CN 111396279 A CN111396279 A CN 111396279A
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- guide rail
- piston
- assembly
- pump core
- pump
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- 230000005540 biological transmission Effects 0.000 claims abstract description 33
- 230000008878 coupling Effects 0.000 claims description 59
- 238000010168 coupling process Methods 0.000 claims description 59
- 238000005859 coupling reaction Methods 0.000 claims description 59
- 230000033001 locomotion Effects 0.000 claims description 23
- 238000007789 sealing Methods 0.000 claims description 13
- 238000009434 installation Methods 0.000 claims description 7
- 230000000712 assembly Effects 0.000 abstract description 5
- 238000000429 assembly Methods 0.000 abstract description 5
- 239000003921 oil Substances 0.000 description 94
- 239000000306 component Substances 0.000 description 13
- 230000009471 action Effects 0.000 description 11
- 238000004891 communication Methods 0.000 description 8
- 239000008358 core component Substances 0.000 description 7
- 230000001133 acceleration Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 239000010720 hydraulic oil Substances 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance 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
- 230000002441 reversible effect Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
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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
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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
- F04B1/124—Pistons
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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
- 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
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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
- 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
Abstract
The force balance type two-dimensional piston pump comprises a front end cover, an upper coupler assembly, an upper pump core assembly, a pump shell, a middle coupler assembly, a lower 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, and 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, a piston and a pump core cylinder body in the pump core body enclose to form a right closed cavity; the left piston ring, the piston and the pump core cylinder body enclose to form a left closed cavity; the right closed cavity is communicated with a first distribution groove of the piston, and the left closed cavity is communicated with a second distribution groove of the piston; the mass sum of the balance rotor composed of 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 composed of the left guide rail, the right guide rail and the piston.
Description
Technical Field
The invention relates to a hydraulic plunger pump, belonging 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, hydraulic pumps have been widely applied in important fields such as aerospace, marine ships and the like. The traditional 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, size and the like.
The conventional common axial plunger pump has many internal relatively-moving parts, high requirements on material and processing precision, sensitivity to oil pollution, high requirements and cost on processing, use and maintenance and high price; the cylinder body rotates along with the transmission shaft, and the rotational inertia is large, so that the response speed of starting, stopping and speed regulation is low, and the control of the output flow of the pump by the speed regulation is not facilitated; the friction pair in the cylinder body is more, the temperature rise of the cylinder body is faster under the high-speed rotation, and the abrasion of parts such as a valve plate, a plunger and the like directly influences the service life and the durability of the pump. In addition, due to the limitation of the working principle of the plunger pump, the transmission shaft rotates for a circle, each plunger can only realize oil absorption and oil discharge once, and the displacement of the plunger is limited.
Because of various defects of the conventional plunger pump, patent document CN205895515U proposes a hydraulic pump with a novel structure, which can rotate by using the motion principle of two degrees of freedom of a piston and can move axially to realize the oil sucking and discharging functions, and is named as a two-dimensional 2D piston pump because it has two-dimensional motion during operation. The two-degree-of-freedom motion principle is applied to the design of a piston of the 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 type transmission mode to realize the reciprocating 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 capacity and high volumetric efficiency. However, the two-dimensional 2D double piston pump has disadvantages in terms of high speed, operation stability and heavy load.
Disclosure of Invention
In order to overcome the defects of the conventional two-dimensional 2D piston pump, the invention provides the force balance type two-dimensional 2D axial plunger pump which utilizes the two degrees of freedom of the plunger and can axially move while the plunger rotates so as to realize the continuous oil suction and discharge functions.
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 pump core assembly, a pump shell, an intermediate coupler assembly, a lower 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 by a long straight oil duct, and the long straight oil duct is communicated with an oil outlet of the pump shell. The pump case oil inlet and the pump case oil outlet are respectively positioned on the opposite sides of the pump case.
The pump case inner cavity is formed by enclosing the pump case, an upper pump core assembly at the left end of the pump case and a lower pump core assembly at the right end of the pump case.
The upper pump core assembly and the lower pump core assembly respectively comprise a pump core body installed 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 are opposite in axial direction of the installation direction. The pump core body comprises a left guide rail assembly, a right guide rail assembly and a pump core assembly. And 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 and a pair of high-pressure columns, the low-pressure columns are arranged along a first diameter of the pump core cylinder body, the high-pressure columns are arranged along a second diameter of the pump core cylinder body, and the first diameter and the second diameter are perpendicular to each other and are located at different positions of an axial lead. The low-pressure column is provided with a U-shaped groove at one end close to the axial lead, 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 conical roller through a bearing; the pump core cylinder body comprises an outer ring and an inner ring which are concentrically arranged, the inner ring is provided with a pair of oil outlet holes and a pair of oil inlet holes, the oil outlet holes and the oil inlet holes are rectangular holes which are circumferentially and uniformly distributed at intervals, the oil inlet holes are communicated with the U-shaped groove of the low-pressure column, and the oil outlet holes are communicated with the inner hole of the high-pressure column; the outer ring is provided with mounting holes of a high-pressure column and a low-pressure column, wherein the mounting holes of the high-pressure column are communicated with an annular groove on the inner wall of the pump shell.
The piston assembly penetrates through the inner ring along the axial lead direction and comprises a transmission shaft, a left piston ring, a right piston ring and a piston. Step wall surfaces are formed on two sides of the piston, a pair of first flow distribution grooves and a pair of second flow distribution grooves are formed in the wall surface of the piston, the first flow distribution grooves and the second flow distribution grooves are alternately and uniformly distributed, the first flow distribution grooves and the second flow distribution grooves are U-shaped flow distribution grooves with opposite axial openings, and the width of each U-shaped flow distribution groove is consistent with that of a rectangular hole in the inner ring. The left piston ring and the right piston ring are respectively sleeved on steps on two sides of the piston, and the mounting directions are opposite in axial direction. The excircle of the transmission shaft is in clearance fit with the inner circle of the piston, and the transmission shaft and the piston move axially and 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 assembly and the right guide rail assembly are identical in structure and opposite in axial direction. The pump core cylinder body assembly is characterized in that one side close to the pump core cylinder body assembly is used 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 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-adding 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 the equal-adding equal-deceleration curved surfaces of the left balance guide rail and the right balance guide rail correspond to each other. 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 and 2 lowest points of the equal-acceleration and equal-deceleration curved surfaces of the left guide rail and the right guide rail correspond to each other. The phases of the equal-adding equal-deceleration curved surfaces of the left balance guide rail and the left guide rail are circumferentially staggered by 90 degrees, namely the lowest point of the equal-adding equal-deceleration curved surface of the left balance guide rail corresponds to the highest point of the equal-adding equal-deceleration curved surface of the left guide rail. The phases of the equal-adding 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-adding equal-deceleration curved surface of the right balance guide rail corresponds to the highest point of the equal-adding equal-deceleration curved surface of the right guide rail.
And a right piston ring, a piston and a pump core cylinder body in the pump core body enclose a right closed cavity. The piston is characterized in that one side close to the pump core cylinder body is used as the inner side, the outer circle of the inner side of the right piston ring and the outermost circle of the middle of the piston are flush and matched with the inner ring of the pump core cylinder body in a clearance mode, and the inner circle of the inner side of the right piston ring and the outer circle of the right step of the piston are matched with each other in a clearance mode. A left piston ring, a piston and a pump core cylinder body in the pump core body enclose a left closed cavity, and the sealing mode of each part is consistent with that of a right closed cavity. The right closed cavity is always communicated with a first distribution groove of the piston, and the left closed cavity is always communicated with a second distribution groove of the piston.
The mass sum of the balance rotor composed of 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 composed of the left guide rail, the right guide rail and the piston.
The intermediate coupling component is connected with the right guide rail component in the upper pump core component and the same-name guide rail component in the lower pump core component respectively through a shifting fork structure, so that the intermediate coupling component and the right guide rail component can rotate synchronously in the circumferential direction and can slide relatively in the axial direction. Each part of the upper pump core assembly and the like parts of the lower pump core assembly are in circumferential phase difference of 45 degrees.
The left end of the upper coupling assembly is axially fixed with the front end cover through a bearing and a sealing ring, the right end of the upper coupling assembly is connected with a left guide rail assembly in the upper pump core assembly through a shifting fork structure, and the upper coupling assembly and the left guide rail assembly of the upper pump core assembly synchronously rotate and simultaneously realize free relative axial movement.
According to the force balance type two-dimensional piston pump, oil enters the cavity in the pump shell from the oil inlet below the pump shell. The left end of the containing cavity is sealed by an upper pump core assembly and a pump shell through a sealing piece, and the right end of the containing cavity is sealed by a lower pump core assembly and a pump shell through a sealing piece. The oil in the containing cavity flows through the U-shaped groove of the low-pressure column to reach the oil inlet of the pump core cylinder body.
When the pair of conical rollers fixed on the high-pressure column is in contact with the lowest point of the curved surface of the left guide rail and the highest point of the curved surface of the left balance guide rail, the pair of conical rollers fixed on the low-pressure column is in contact with the highest point of the curved surface of the right guide rail and the lowest point of the right balance guide rail. And in the process that the curved surface of the left guide rail turns 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 curved surface of the right guide rail to turn from the highest point to the lowest point. And in the process that the right balance guide rail turns to the highest point from the lowest point, the right piston ring and the transmission shaft are driven to rotate in the same direction and move rightwards, the transmission shaft drives the left balance guide rail to turn to the lowest point from the highest point, and the left balance guide rail drives the left piston ring to rotate in the same direction and move rightwards. The piston rotates in the circumferential direction, so that the first distribution groove is 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.
And in the process that the curved surface of the left balance guide rail turns 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. And in the process that the curved surface of the right guide rail turns from the lowest point to the highest point, the piston is driven to rotate in the same direction and move rightwards, 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 in the circumferential direction, so that the first distributing groove is communicated with the oil outlet of the pump core cylinder body. The piston moves rightwards and the right piston ring moves leftwards to enable the upper-connection right sealing cavity to be compressed, and compressed high-pressure oil enters the inner hole of the high-pressure column when communicating with the oil outlet hole of the pump core cylinder body through the first distributing groove. High-pressure oil in the inner hole of the high-pressure column is converged at annular grooves on the left side and the right side of the pump shell and then flows out of an oil outlet above the pump shell through the long straight oil passage.
The left closed cavity sucks and discharges oil in the same way as the right closed cavity, but the phases are opposite.
Because the circumferential phase difference of the upper pump core assembly and the lower pump core assembly is 45 degrees, the oil pumping curves of the upper pump core assembly and the lower pump core assembly are opposite, so that the fluctuation of the pumped oil quantity is partially offset, and the oil output quantity is relatively balanced.
The mass sum of the balance rotor composed of 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 composed of the left guide rail, the right guide rail and the piston, the two rotors axially move in opposite directions according to the law, and the inertia force generated by the axial reciprocating motion of the two rotors is offset.
Furthermore, the front end cover is fixedly connected to the left end face of the pump shell through a bolt, and the rear end cover is fixedly connected to the right end face of the pump shell through a bolt.
Further, the pump core body of the upper pump core assembly and the pump core body of the lower pump core assembly are installed on two sides of the pump shell through threads, and the installation directions are opposite in axial direction.
Under the connection of the intermediate coupling assembly, the equal deceleration curved surface of the right guide rail assembly in the upper coupling pump core assembly and the equal deceleration curved surface of the right guide rail assembly in the lower coupling pump core assembly have a phase difference of 45 degrees, namely the highest point of the right guide rail equal deceleration curved surface in the upper coupling pump core assembly corresponds to the middle point of the right guide rail equal deceleration curved surface in the lower coupling pump core assembly.
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, and the installation directions are opposite along the axial direction. The axial direction of the invention is along the axial lead direction, and the axial lead of the invention is on the central axis of the pump shell.
Furthermore, 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 retainer ring, and the right side of the right concentric ring is provided with a right retainer ring.
Further, concentric rings are arranged between the inner ring of the pump core cylinder body and the left piston ring and between the right piston ring and the piston, 2 pairs of rectangular holes which are uniformly distributed in the circumferential direction are formed in the concentric rings and 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 the concentric ring, and the oil outlet hole of the pump core cylinder body corresponds to the high-pressure hole of the.
The invention has the following beneficial effects:
1. the volume change is completed by the cooperation of the piston and the piston ring, which is doubled compared with the volume change of a single piston and saves space. When the stroke and the discharge capacity are not changed, the cross-sectional area is reduced, the stress of the guide rail and the conical roller is reduced, and high load is easy to realize.
2. The structure that the left piston ring, the right piston ring, the piston, the transmission shaft, the guide rail and the balance guide rail are matched with each other is provided for balancing the inertia force, reducing the mechanical vibration during the operation, enabling the output rotating speed of the motor to be more stable and reducing the flow pulsation. Meanwhile, the output torque of the motor can be reduced, and energy is saved.
3. The transmission part is lubricated in oil liquid, the mechanical efficiency is high, and the abrasion is reduced.
Drawings
Fig. 1 is an assembly schematic of the present invention.
Fig. 2 is a schematic view of the pump casing structure of the present invention.
FIG. 3 is a schematic view of the assembly of the present invention.
Fig. 4 is a schematic view of the upper pump core assembly of the invention.
Fig. 5 a-5 b are schematic views of a pump cartridge cylinder assembly of the present invention. Wherein fig. 5a is a schematic view of a portion of the assembly of the pump core cylinder of the present invention and fig. 5b is an exploded view of the pump core cylinder assembly of the present invention.
Fig. 6a to 6c are views of the piston assembly of the present invention, and fig. 6c corresponds to a sectional line a-a of fig. 6 b. Wherein fig. 6a is a front view of a piston assembly of the present invention, fig. 6b is a top view of a piston assembly of the present invention, and fig. 6c is a cross-sectional view of a piston of the present invention.
Fig. 7a to 7d are sectional views of the upper pump core assembly and the pump casing of the present invention. Fig. 7a is a schematic view of an upper coupling right closed cavity of the present invention, fig. 7b is a schematic view of an upper coupling left closed cavity of the present invention, fig. 7c is a top sectional view of an upper coupling core assembly and a pump casing, and fig. 7d is a front sectional view of an upper coupling core assembly and a pump casing.
Fig. 8 a-8 b are assembly views of the upper left and right rail assemblies of the present invention. Wherein fig. 8a is a front view of the assembly of the upper left and right rail assemblies of the present invention, and fig. 8b is a top view of the assembly of the upper left and right rail assemblies of the present invention.
Fig. 9 a-9 b are views of the upper left guide rail of the present invention. Wherein fig. 9a is a front view of the upper left guide rail of the present invention, and fig. 9b is a left view of the upper left guide rail of the present invention.
Fig. 10a to 10c are three views of the upper left balance rail according to 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 the upper coupling assembly of the present invention.
Fig. 13a to 13c are schematic views of an intermediate coupling assembly according to 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 view of the present invention.
Fig. 15a to 15d are sectional views of the flow channel rotated by 0 to 180 degrees according to the present invention, corresponding to the sectional line a-a in fig. 14. Wherein fig. 15a is a sectional view of a flow channel of the present invention turned to 0 ° 180 °, fig. 15b is a sectional view of a flow channel of the present invention turned to 45 °, fig. 15c is a sectional view of a flow channel of the present invention turned to 90 °, and fig. 15d is a sectional view of a flow channel 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 coupling pump core assembly 3, a pump shell 4, an intermediate coupler assembly 5, a lower coupling 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 and lower coupling core assemblies 3 and 6, whereby the intermediate coupling assembly 5 is axially fixed for rotation within the pump housing 4. The left end of the upper coupling component 2 is axially fixed with the front end cover 1 through a bearing and a sealing ring, the right end of the upper coupling component 2 is restrained by the upper coupling pump core component 3, and therefore the upper coupling component 2 is axially fixed and can rotate in the circumferential direction in the pump shell 4.
The left side and the right side of the interior of the pump shell 4 are respectively provided with an annular groove, and the annular grooves comprise a left annular groove 4A and a right annular groove 4E. The left annular groove 4A and the right annular groove 4E are communicated through 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. An oil inlet 4C and an 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 are opposite in axial direction of the installation direction. 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 cartridge assembly 9 includes a pump cartridge cylinder assembly 91 and a piston assembly 92.
The pump core cylinder assembly 91 includes a pair of low pressure columns 912 disposed along a first diameter of the pump core cylinder 915 and a pair of high pressure columns 914 disposed along a second diameter of the pump core cylinder 915, the first and second diameters being perpendicular to each other and located at different positions on the axis. One end of the low-pressure column 912 close to the axial lead 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 the first cone roller 911 through a bearing, and the high pressure column 914 is connected to the second cone roller 913 through a bearing. The pump core cylinder 915 comprises an outer ring 91H and an inner ring 91E which are concentrically arranged, a pair of oil inlet holes 91F and a pair of oil outlet holes 91G are formed in the inner ring 91E, the oil outlet holes 91G and the oil inlet holes 91F are rectangular holes which are circumferentially and alternately and uniformly 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 the high-pressure column 914 and a mounting hole 91D of the 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 ring. The left track assembly 8 is in contact with only the second cone roller 913 and the right track assembly 10 is in contact with only the first cone roller 911.
The piston assembly 92 penetrates through the inner ring 91E along the axis line direction and comprises 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. The concentric ring 928 is provided with 2 pairs of rectangular holes which are circumferentially and alternately distributed uniformly, namely a low-pressure hole 92C and a high-pressure hole 92D, and the excircle of the concentric ring 928 is in interference fit with the inner ring 91E of the pump core cylinder body 915. Rectangular splines are arranged at two ends of the piston 925, 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 or 92C of the concentric rings 928. The left concentric ring 924 and the right concentric ring 926 are respectively sleeved on the first-stage steps 92B on both sides of the piston 925 in a clearance fit manner. The left retainer ring 923 and the right retainer ring 927 are respectively sleeved on the second-stage steps 92A on two sides of the piston 925 in an interference fit manner to respectively fix the left concentric ring 924 and the right concentric ring 926. The first step 92B is located between the piston 925 and the second step 92A. The pump core cylinder body is arranged on the inner side of the cylinder body, the outer side of the left piston ring 922 and the outer side of the right piston ring 929 are both of a U-shaped structure, the inner side of the cylinder body is of an annular structure, the U-shaped structure on 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 on 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 ring structure on the inner side of the left piston ring 922 is in clearance fit with the outer circle of the left concentric ring 924, the inner circle of the ring structure on the inner side of 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 move axially and relatively. The transmission shaft 921 is connected to the left balance rail 81 on the left rail assembly 8 and the right balance rail 102 on the right rail assembly 10 through rectangular keys at both ends, and the piston 925 is connected to the left rail 82 on the left rail assembly 8 and the right rail 101 on the right rail assembly 10 through rectangular keys at both ends. The transmission shaft 921 and the piston 925 make opposite axial reciprocating motions while making circumferential motions in the same direction under the constraint of the left guide rail assembly 8 and the right guide rail assembly 10.
The right piston ring 929, the right concentric ring 926, the piston 925, and the concentric ring 928 in the pump core body enclose a right enclosed cavity B1. And a gap is sealed between the inner circle of the concentric ring 928 and the outer circle of the inner side of the right piston ring 929. A gap seal is provided between the inner circle of the concentric ring 928 and the outer circle of the piston 925. And a gap is sealed 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 all parts are sealed in the same way as a right closed cavity B1. The right closed chamber B1 is always in communication with the first distribution grooves a, B of the piston 925, and the left closed chamber a1 is always in communication with the second distribution grooves c, d of the piston 925. The low pressure hole 92C of the concentric ring 928 is communicated with the oil inlet hole 91F of the pump core cylinder 915, and the high pressure hole 92D of the concentric ring 928 is communicated with the oil outlet hole 91G of the pump core cylinder 915. The piston 925 rotates circumferentially and reciprocates axially in the concentric ring 928 under the constraint of the left guide rail assembly 8 and the right guide rail assembly 10, so that the piston 925 and the pump core cylinder body 915 are in flow distribution and oil inlet and outlet.
According to the force balance type two-dimensional piston pump, oil enters the cavity 4F in the pump shell 4 from the oil inlet 4C below the pump shell 4. The oil in the chamber 4F flows through the U-shaped groove 91A of the low pressure column 912 to the oil inlet 91F of the pump core cylinder 915. The piston 925 rotates both circumferentially and reciprocates axially, and when the first metering grooves a, B communicate with the low pressure ports 92C of the concentric ring 928, oil enters the right seal chamber B1. When the right sealing cavity B1 is compressed, the oil inside is pressurized into high-pressure oil; the first metering slots a, B now communicate with the high pressure port 92D in the concentric ring 928 and high pressure oil enters the bore 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 passes through the annular groove 4A on the left side of the pump shell 4 and then flows through the long straight oil passage 4D to flow out of 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 passes through the annular groove 4E on the right side of the pump shell 4 and then flows through the long straight oil passage 4D to flow out of the oil outlet 4B above the pump shell 4. The left closing chamber a1 draws and discharges oil in the same manner as the right closing chamber B1, but the phase of the oil pumping curve is reversed.
The left guide rail assembly 8 comprises a left guide rail 82 and a left balance guide rail 81, and the right guide rail assembly 10 comprises a right guide rail 101 and a right balance guide rail 102. The left guide rail assembly 8 and the right guide rail assembly 10 are identical in structure and opposite in axial direction. Taking the side close to the pump core cylinder block assembly 91 as the inner side, the track surfaces of the right guide rail 101 and the right balance guide rail 102 and the left guide rail 82 and the left balance guide rail 81 are both disposed inward, the first tapered roller 911 rolls on the right guide rail 101 and the right balance guide rail 102, and the second tapered roller 913 rolls on the left guide rail 82 and the left balance guide rail 81.
The left guide rail 82 is circular, the inner side of the left guide rail is a working surface conforming to the equal acceleration and equal deceleration curves, the outer side of the left guide rail is U-shaped, the center of the left guide rail is provided with a rectangular key groove, and the working curved 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 circular, the inner side of the left balance guide rail 81 is a working surface conforming to the equal acceleration and equal deceleration curves, the working surface is matched with the corresponding second cone roller 913 to rotate, the outer side of the left balance guide rail 81 is provided with 2 pairs of first slots 8B and second slots 8C which are alternately distributed, the first slot 8C is used for installing the left guide rail 82, the second slot 8B and a pair of holes 8A formed in two sides are used for connecting a left piston ring 922, and the center of the end surface of the left balance guide rail 81 is provided with a rectangular key groove. After the left guide rail 82 is arranged 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 component 8 of the upper pump core component 3 are used for mounting the upper coupling component 2; the middle coupling component 5 is arranged in the installation groove 8D of the right guide rail component 10 of the upper pump core component 3 and the installation groove 8D of the right guide rail component 10 of the lower pump core component 6.
The left guide rail 82 and the right guide rail 101 are respectively fixed at both ends of the piston 925 by rectangular keys. 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 phases of the equal-adding deceleration curved surfaces of the left balance guide rail 81 and the right balance guide rail 102 are consistent, the phases of the equal-adding deceleration curved surfaces of the left guide rail 82 and the right guide rail 101 are consistent, and the phases of the equal-adding deceleration curved surfaces of the left balance guide rail 81 and the left guide rail 82 are circumferentially staggered by 90 degrees.
The left guide rail 82 moves circumferentially, 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 axially reciprocate while rotating circumferentially in the concentric ring 928; meanwhile, the left balance guide rail 81 performs circumferential rotation, and under the constraint of the first cone roller 911 and the second cone roller 913, 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 perform circumferential synchronous rotation and axial reciprocating motion simultaneously. The axial motion of the balance rotor composed of 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 opposite to the axial motion of the rotor composed of the left guide rail 82, the right guide rail 101 and the piston 925. That is, in the axial direction, the left guide rail 82 and the right guide rail 101 move with acceleration such as curved surfaces, and the left balance guide rail 81 and the right balance guide rail 102 move with acceleration such as curved surfaces, and the axial movement directions of the two are opposite; the left guide rail 82 and the right guide rail 101 move in a speed reducing mode in a curved surface mode and the like, the left balance guide rail 81 and the right balance guide rail 102 move in a speed reducing mode in a curved surface mode and the like, and the axial movement directions of the left balance guide rail 81 and the right balance guide rail 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 inertia force generated by the axial reciprocating motion of the two rotors is counteracted through the regular axial reverse motion.
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 is hollowed. Go up shaft coupling 21 and the left guide rail subassembly 8 of last pump core subassembly 3 adopts following shift fork structure interconnect: put into the round pin axle in order to fix 4 first flat gyro wheels 22 in 4 through-holes 2C of last shaft coupling 21, 4 first flat gyro wheels 22 are put into the mounting groove 8D of the left rail set spare 8 of upper pump core subassembly 3. Go up the shaft coupling and lead to groove 2A, 2B and provide dodging the space for the left guide rail assembly 8 of upper coupling pump core subassembly 3. So that the left guide rail assembly 8 of the upper pump core assembly 3 can realize free relative axial movement while keeping synchronous rotation.
The intermediate coupling assembly 5 comprises a stop collar 51, an intermediate coupling 52 and 8 second flat rollers 53. The limiting sleeve 51 is a circular ring, and the inner circle of the limiting sleeve is in interference fit with the outer circle of the intermediate coupler 52. The left side of the outer surface of the intermediate coupling 52 is provided with 4 left side round holes 5B distributed in the circumferential direction, the right side of the outer surface of the intermediate coupling is provided with 4 right side round holes 5E distributed in the circumferential direction, the left side round holes 5B and the right side 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 distributed in an alternating manner, and the right end face is provided with 2 pairs of right end grooves 5D and 5F distributed in an alternating manner.
The intermediate coupling 52 and the right guide rail assembly 10 of the upper coupling pump core assembly 3 are connected with each other by adopting the following shifting fork structure: and a pin shaft is placed in a left round hole 5B of the middle 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 guide rail assembly 10 of the upper coupling pump core assembly 3. The intermediate coupling 52 and the right guide rail assembly 10 of the lower coupling pump core assembly 6 are connected with each other by adopting the following shifting fork structure: and a pin shaft is placed in a right round hole 5E of the middle 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 guide rail assembly 10 of the lower coupling pump core assembly 6.
The left end grooves 5A and 5C of the intermediate coupling 52 provide an avoiding 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 and 5F provide an avoiding 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-adding deceleration curved surface of the right guide rail assembly 10 of the upper coupling pump core assembly 3 and the equal-adding deceleration curved surface of the right guide rail assembly 10 of the lower coupling pump core assembly 6 form a phase difference of 45 degrees.
Principle of operation
According to the force balance type two-dimensional piston pump, oil enters the cavity 4F in the pump shell 4 from the oil inlet 4C below the pump shell 4. The oil in the chamber 4F flows through the U-shaped groove 91A of the low pressure column 912 to the oil inlet 91F of the pump core cylinder 915. The piston 925 rotates circumferentially so that the first metering grooves a, B communicate with the low pressure ports 92C of the concentric ring 928 and oil enters the seal chamber B1. When the right seal chamber B1 is compressed, the oil inside is pressurized to high pressure oil, and the first distributing grooves a, B communicate with the high pressure hole 92D on the concentric ring 928, and the high pressure oil enters the inner hole 91B of the high pressure column 914. After the high-pressure oil in the inner hole 91B of the high-pressure column 914 of the upper pump core assembly 3 is gathered 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 gathered at the annular groove 4E on the right side of the pump shell 4, the high-pressure oil flows through the long straight oil passage 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 subsequent movement thereof is as shown in fig. 15a to 15 d.
At the beginning, 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 position of the axial stroke. At the moment, the volumes of the hydraulic oil contained in the right closed cavity B1 and the left closed cavity A1 are equal; the first metering grooves a, b on the piston 925 communicate with the low pressure holes 92C of the concentric ring 928 and the second metering grooves C, D on the piston 925 communicate with the high pressure holes 92D of the concentric ring 928, with the openings in a fully open position, i.e., with the largest communication area. The left guide rail assembly 8 in the upper coupling core assembly 3 is rotated clockwise as shown in fig. 14 by the upper coupling assembly 2. Under the action of the right balance guide rail 102, the right piston ring 929 moves rightwards along the axial stroke, under the action of the left guide rail 82 and the right guide rail 101, the piston 925 moves leftwards along the axial stroke to enable the right closed cavity B1 to be gradually enlarged, hydraulic oil flows in through the U-shaped groove 91A and enters the right closed cavity B1 from the low-pressure hole 92C of the concentric ring 928 through the first distributing grooves a and B. Meanwhile, under the action of the left balance guide rail 81, the left piston ring 922 moves rightwards along the axial stroke, the piston 925 moves leftwards to enable the left closed cavity A1 to become smaller gradually, and high-pressure oil flows out from the left closed cavity A1 through the second distributing grooves c and D, the high-pressure hole 92D of the concentric ring 928, the inner hole 91B, the left annular groove 4A, the long straight oil passage 4D and the oil outlet 4B. The piston 925 axially reciprocates and circumferentially rotates by the left guide rail 82 and the right guide rail 101, and its axial displacement corresponds to a deceleration curve such as an equal acceleration. As the piston 925 moves to the left along its axial stroke, it simultaneously rotates in the direction shown in fig. 15 a. The areas of communication between the first distributing grooves a, b and the low-pressure holes 92C of the concentric rings 928, and between the second distributing grooves C, D and the high-pressure holes 92D of the concentric rings 928 become smaller. The piston 925 of the upper pump core assembly 3 continues to move leftwards along the axial stroke under the action of the left guide rail 82 and the right guide rail 101, and the left piston ring 922 and the right piston ring 929 continue to move rightwards along the axial stroke under the action of the left balance guide rail 81 and the right balance guide rail 102 respectively.
After the piston 925 of the upper pump core assembly 3 rotates by 45 degrees, the piston 925 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, the volume of the right closed cavity B1 reaches the maximum at the moment, the volume of the left closed cavity A1 reaches the minimum, the communication area between the first distributing grooves a and B of the piston 925 and the low-pressure hole 92C of the concentric ring 928 and the communication area between the second distributing grooves C and D and the high-pressure hole 92D of the concentric ring 928 are completely closed, and oil contained in the left closed cavity A1 and the right closed cavity B1 is not communicated with oil contained in the accommodating cavity 4F and the inner hole 91B. The piston 925 of the upper pump core assembly 3 starts moving along the axial stroke to the right under the action of the left guide rail 82 and the right guide rail 101, and the left piston ring 922 and the right piston ring 929 start moving along the axial stroke to the left under the action of the left balance guide rail 81 and the right balance guide rail 102 respectively.
After the piston rotates by 90 degrees, 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 volume of the left closed cavity A1 is equal to that of the right closed cavity B1, and the first distributing grooves a and B of the piston 925, the high-pressure hole 92D of the concentric ring 928, the second distributing grooves C and D of the concentric ring 928 and the low-pressure hole 92C of the concentric ring 928 are in a state of being completely opened, namely the communicating area is the largest. Hydraulic oil flows in through the U-shaped groove 91A from the low pressure port 92C of the concentric ring 928 through the second distribution grooves C, d into the left closed chamber a 1. High-pressure oil flows out from the right closed cavity B1 through the first distributing grooves a and B, the high-pressure hole 92D of the concentric ring 928, the inner hole 91B, the left annular groove 4A, the long straight oil passage 4D and the oil outlet 4B. The piston 925 in the upper pump core assembly 3 continues to move to the right along the axial stroke under the action of the left guide rail 82 and the right guide rail 101, and the left piston ring 922 and the right piston ring 929 continue to move to the left along the axial stroke under the action of the left balance guide rail 81 and the right balance guide rail 102 respectively.
After the rotation of 135 degrees, the piston 925 in the upper pump core component 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 cavity B1 reaches the minimum, the communication area between the first distributing grooves a and B of the piston 925 and the high-pressure hole 92D of the concentric ring 928 and the communication area between the second distributing grooves C and D and the low-pressure hole 92C of the concentric ring 928 are completely closed, and oil contained in the left closed cavity A1 and the right closed cavity B1 is not communicated with oil contained in the cavity 4F and the inner hole 91B. The piston 925 in the upper pump core assembly 3 starts moving to the left along an axial stroke under the action of the left guide rail 82 and the right guide rail 101, and the left piston ring 922 and the right piston ring 929 start moving to the right along an axial stroke under the action of the left balance guide rail 81 and the right balance guide rail 102 respectively.
After 180 degrees of rotation, the position and the movement trend of the moving part in the force balance type two-dimensional piston pump are the same as 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 positions are 45 degrees.
When any one of the pistons 925 completes its reciprocating motion every 360 degrees, it sucks and discharges oil 2 times. The two pistons 925 complete reciprocating motions twice with 4 times of oil suction and oil discharge each, while rotating 360 degrees in one revolution.
The embodiments described in this specification are merely illustrative of implementations of the inventive concept and the scope of the present invention should not be considered limited to the specific forms set forth in the embodiments but rather by the equivalents thereof as may occur to those skilled in the art upon consideration of the present inventive concept.
Claims (5)
1. The force balance type two-dimensional piston pump comprises a front end cover, an upper coupler assembly, an upper pump core assembly, a pump shell, a middle coupler assembly, a lower 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 by 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 on the opposite sides of the pump shell;
the pump shell inner cavity is formed by enclosing a pump shell, an upper pump core assembly at the left end of the pump shell and a lower pump core assembly 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 are opposite in the axial direction of the mounting 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 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 and a pair of high-pressure columns, the low-pressure columns are arranged along a first diameter of the pump core cylinder body, the high-pressure columns are arranged along a second diameter of the pump core cylinder body, and the first diameter and the second diameter are perpendicular to each other and are positioned at different positions of an axial lead; one end of the low-pressure column close to the axial lead is provided with a U-shaped groove, 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 conical roller through a bearing; the pump core cylinder body comprises an outer ring and an inner ring which are concentrically arranged, the inner ring is provided with a pair of oil outlet holes and a pair of oil inlet holes, the oil outlet holes and the oil inlet holes are rectangular holes which are circumferentially and uniformly distributed at intervals, the oil inlet holes are communicated with the U-shaped groove of the low-pressure column, and the oil outlet holes are communicated with the inner hole of the high-pressure column; the outer ring is provided with mounting holes of a high-pressure column and a low-pressure column, wherein the mounting hole of the high-pressure column is communicated with an annular groove on the inner wall of the pump shell;
the piston assembly penetrates through the inner ring along the axial lead direction and comprises a transmission shaft, a left piston ring, a right piston ring and a piston; step wall surfaces are formed on two sides of the piston, a pair of first flow distribution grooves and a pair of second flow distribution grooves are formed in the wall surface of the piston, the first flow distribution grooves and the second flow distribution grooves are alternately and uniformly distributed, the first flow distribution grooves and the second flow distribution grooves are U-shaped flow distribution grooves with opposite axial openings, and the width of the U-shaped flow distribution grooves is consistent with that of rectangular holes in the inner ring; the left piston ring and the right piston ring are respectively sleeved on steps on two sides of the piston, and the mounting directions are opposite axially; the excircle of the transmission shaft is in clearance fit with the inner circle of the piston, and the transmission shaft and the piston move axially and 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 assembly and the right guide rail assembly have the same structure and are opposite in axial direction; 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 arranged inwards, the conical rollers connected to the high-pressure column roll on the right guide rail and the right balance guide rail, and the conical rollers connected to the low-pressure column roll 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 a left piston ring, the right balance guide rail is connected with a 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-adding 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 the equal-adding equal-deceleration curved surfaces of the left balance guide rail and the right balance guide rail correspond to each other; the phases of the equal-adding equal-deceleration curved surfaces of the left guide rail and the right guide rail are consistent, namely 2 highest points and 2 lowest points of the equal-adding equal-deceleration curved surfaces of the left guide rail and the right guide rail correspond to each other; the phases of the equal-adding equal-deceleration curved surfaces of the left balance guide rail and the left guide rail are circumferentially staggered by 90 degrees, namely the lowest point of the equal-adding equal-deceleration curved surface of the left balance guide rail corresponds to the highest point of the equal-adding equal-deceleration curved surface of the left guide rail; the phases of the equal-adding 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-adding equal-deceleration curved surface of the right balance guide rail corresponds to the highest point of the equal-adding equal-deceleration curved surface of the right guide rail;
the right piston ring, the piston and the pump core cylinder body in the pump core body enclose a right closed cavity; the side close to the pump core cylinder body is taken as the inner side, the outer circle of 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 ring of the pump core cylinder body, and the inner circle of the inner side of the right piston ring is in clearance fit with the outer circle of the right step of the piston; a left piston ring, a piston and a pump core cylinder body in the pump core body enclose a left closed cavity, and the sealing mode of each part is consistent with that of a right closed cavity; the right closed cavity is always communicated with a first flow distribution groove of the piston, and the left closed cavity is always communicated with a second flow distribution groove of the piston;
the mass sum of a balance rotor consisting of 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 consisting of the left guide rail, the right guide rail and the piston;
the middle coupling assembly is respectively connected with a right guide rail assembly in the upper pump core assembly and a same-name guide rail assembly in the lower pump core assembly through a shifting fork structure, so that the middle coupling assembly and the right guide rail assembly synchronously rotate in the circumferential direction and can relatively slide in the axial direction; each part of the upper pump core assembly and the like part of the lower pump core assembly are circumferentially phase-difference of 45 degrees;
the left end of the upper coupling assembly is axially fixed with the front end cover through a bearing and a sealing ring, the right end of the upper coupling assembly is connected with a left guide rail assembly in the upper pump core assembly through a shifting fork structure, and the upper coupling assembly and the left guide rail assembly of the upper pump core assembly synchronously rotate and simultaneously realize free relative axial movement.
2. The force-balanced, two-dimensional piston pump of claim 1, wherein: the front end cover is fixedly connected to the left end face of the pump shell through a bolt, and the rear end cover is fixedly connected to the right end face of the pump shell through a bolt.
3. The force-balanced, two-dimensional piston pump of claim 1, wherein: the pump core body of the upper pump core assembly and the pump core body of the lower pump core assembly are installed on two sides of the pump shell through threads, and the installation directions are opposite in axial direction.
4. The force-balanced, two-dimensional piston pump of 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 retainer ring, and the right side of the right concentric ring is provided with a right retainer ring.
5. The force-balanced, two-dimensional piston pump of claim 1, wherein: the concentric ring is equipped with between pump core cylinder body inner circle and the left and right piston ring and the piston, it has 2 pairs of circumference equipartition's rectangular hole to open on the concentric ring, is low pressure hole and high-pressure hole respectively, and the excircle of concentric ring and the through-hole inner wall interference fit of pump core cylinder body, the inlet port of pump core cylinder body and the low pressure hole of concentric ring correspond, and the oil outlet of pump core cylinder body corresponds with the high-pressure hole of concentric ring, intercommunication.
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 true CN111396279A (en) | 2020-07-10 |
| CN111396279B CN111396279B (en) | 2024-02-13 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
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| CN201811533199.9A Active CN111396279B (en) | 2018-12-14 | 2018-12-14 | Force balance type two-dimensional plunger pump |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112610438A (en) * | 2020-11-23 | 2021-04-06 | 河南航天液压气动技术有限公司 | Piston pump |
| CN114198277A (en) * | 2021-12-14 | 2022-03-18 | 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 |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112610438A (en) * | 2020-11-23 | 2021-04-06 | 河南航天液压气动技术有限公司 | Piston pump |
| CN114198277A (en) * | 2021-12-14 | 2022-03-18 | 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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| CN111396279B (en) | 2024-02-13 |
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