CN112065682A - Pile-up type two-dimensional piston monoblock pump - Google Patents
Pile-up type two-dimensional piston monoblock pump Download PDFInfo
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- CN112065682A CN112065682A CN202011065302.9A CN202011065302A CN112065682A CN 112065682 A CN112065682 A CN 112065682A CN 202011065302 A CN202011065302 A CN 202011065302A CN 112065682 A CN112065682 A CN 112065682A
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- 230000033001 locomotion Effects 0.000 claims abstract description 14
- 238000005096 rolling process Methods 0.000 claims description 12
- 238000007789 sealing Methods 0.000 claims description 6
- 230000000712 assembly Effects 0.000 claims description 4
- 238000000429 assembly Methods 0.000 claims description 4
- 230000000737 periodic effect Effects 0.000 claims description 4
- 239000010410 layer Substances 0.000 claims description 3
- 239000002356 single layer Substances 0.000 claims description 3
- 238000007599 discharging Methods 0.000 abstract description 3
- 238000009826 distribution Methods 0.000 description 34
- 238000000034 method Methods 0.000 description 8
- 238000005299 abrasion Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005315 distribution function Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
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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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
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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
- F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two 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
- F04B53/08—Cooling; Heating; Preventing freezing
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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
- F04B53/14—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
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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
- F04B53/16—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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The laminated column type two-dimensional piston monoblock pump comprises a pump body inner cavity which is formed by enclosing an end cover, a main pump body and an auxiliary pump body, wherein a flower shaft, a ball row, a pump core assembly and a cylindrical roller wheel are arranged in the pump body inner cavity; the outer wall surface of the auxiliary pump body is provided with an auxiliary pump body annular groove for absorbing oil, the outer wall surface of the main pump body is provided with a main pump body annular groove for discharging oil, the pump core assembly comprises a piston ring assembly and a concentric ring assembly, the piston ring assembly comprises a piston ring inner rail, a piston ring outer rail and a piston ring, and the concentric ring assembly comprises a concentric ring inner rail, a concentric ring outer rail, a first concentric ring and a second concentric ring; piston ring, first concentric ring, second concentric ring and main pump body enclose and synthesize two work appearance chambeies about, and piston ring subassembly and concentric ring subassembly coaxial and relative nestification are gone up and are rotated along with the rachis in the rachis, carry out opposite direction's axial reciprocating motion under the restraint of cylinder gyro wheel simultaneously. The invention greatly increases the pump discharge capacity, improves the oil suction characteristic, improves the operation stability and prolongs the service life.
Description
Technical Field
The invention relates to the technical field of hydraulic pumps, in particular to a stacked column type two-dimensional piston single pump.
Background
Power-to-weight ratio generally refers to the ratio of the power a power plant is capable of producing to its plant weight. Compared with mechanical transmission and electric transmission, hydraulic transmission is widely applied to the fields including engineering machinery, aerospace, industrial manufacturing and the like due to the remarkable advantage of high power-weight ratio. The hydraulic pump is an energy power element of a hydraulic system, is a hydraulic core component for converting mechanical energy, and is continuously developed in the direction of high pressure, large flow, high speed and light weight. The power-weight ratio of the hydraulic pump is further improved, the development requirement of a hydraulic system is met, the energy utilization efficiency of the whole hydraulic system can be improved, and the hydraulic pump has obvious significance for the continuous development of a hydraulic technology and the application expansion of the hydraulic system.
Compared with other hydraulic pumps, the plunger pump is easier to realize high pressure and large flow on the basis of keeping higher volumetric efficiency, and is widely applied to high-pressure heavy-load occasions such as aerospace, engineering machinery and the like.
The traditional plunger pump can be divided into an axial plunger pump and a radial plunger pump according to the arrangement form of a plurality of plungers, the reciprocating motion of the plungers in plunger cavities is utilized to realize the size change of a containing cavity so as to finish the oil suction and oil discharge processes, but each time a transmission shaft rotates for one circle, a single plunger can only finish the oil suction and oil discharge processes once, the contradiction between the volume weight and the discharge capacity of a hydraulic pump is difficult to balance in the working mode of multi-plunger single stroke, and the improvement of the power-weight ratio is limited. Meanwhile, because the traditional plunger pump has a plurality of internal moving parts and a complex structure, the rotational inertia is large during high-speed movement, and because the sliding friction pair in the pump body structure is more, the abrasion and the heating of parts are also aggravated, so that the service life and the durability are directly influenced. Due to the defects, the plunger pump is limited to be widely applied.
Patent document CN205895515U proposes a hydraulic pump with a novel structure, which utilizes axial movement of a plunger while rotating to realize the function of oil suction and discharge with single plunger and multiple strokes, integrates the flow distribution function on the plunger, simplifies the structure, greatly reduces the number of sliding friction pairs, and has the advantages of small volume, light weight, large displacement and high volumetric efficiency. It is called a two-dimensional (2D) piston pump because its core principle is two-dimensional motion during operation. However, the two-dimensional (2D) piston pump still has disadvantages in terms of operation stability and heavy load, such as a lack of self-priming capability at the initial start, and it is difficult to increase the number of strokes to increase the displacement so as to further improve the power-to-weight ratio.
Disclosure of Invention
In order to overcome the problems, the invention provides a stacked column type two-dimensional piston monoblock pump which is compact in structure, light in weight and high in volumetric efficiency, can remarkably increase the number of strokes in unit time to realize large displacement, and improves the oil suction characteristic through self-pressurization.
The technical scheme adopted by the invention is as follows: the laminated column type two-dimensional piston monoblock pump comprises an end cover, an auxiliary pump body and a main pump body which are sequentially and coaxially arranged along an axial lead, wherein the end cover is fixedly arranged on the left end face of the auxiliary pump body, the right end of the auxiliary pump body is fixedly connected with the left end of the main pump body, the end cover, the main pump body and the auxiliary pump body jointly enclose a pump body inner cavity, and the pump body inner cavity is provided with a spline shaft, a ball row, a pump core assembly and a cylindrical roller;
defining one end of the end cover as a left end, wherein the axial direction is the direction of the central shaft or the direction parallel to the central shaft, the circumferential direction surrounds the central shaft, the inner side is the direction close to the shaft axis, and the outer side is the direction far away from the shaft axis;
the main pump body is of a double-layer cylindrical structure and comprises an inner cylinder and an outer cylinder which are sequentially sleeved from inside to outside, a part of the left end of the inner cylinder is exposed out of the outer cylinder and extends into the auxiliary pump body, a first annular ring is connected between the right end of the inner cylinder and the outer cylinder, and the inner cylinder, the first annular ring and the outer cylinder are connected into a whole; a plurality of oil duct long through holes for oil discharge are uniformly distributed on the wall surface of the main pump body along the circumferential direction of the position corresponding to the first annular ring, and the oil duct long through holes obliquely penetrate through the outer barrel and the first annular ring to the middle part of the inner barrel; the outer wall surface of the main pump body is circumferentially provided with a main pump body annular groove along the position corresponding to the oil passage long through hole, and the oil passage long through hole is communicated with the main pump body annular groove;
the auxiliary pump body is of a single-layer cylindrical structure, a second annular ring is arranged between the auxiliary pump body and the left end of the inner cylinder, and the auxiliary pump body and the second annular ring are connected into a whole; a plurality of oil duct short through holes for absorbing oil are uniformly distributed on the wall surface of the auxiliary pump body along the circumferential direction, the oil duct short through holes are positioned at the position close to the left end of the second annular ring, an auxiliary pump body annular groove is circumferentially arranged on the outer wall surface of the auxiliary pump body along the position corresponding to the oil duct short through holes, and the oil duct short through holes are communicated with the auxiliary pump body annular groove; the first annular ring is provided with a plurality of main pump body roller cavities at intervals along the circumferential direction, the second annular ring is provided with a plurality of auxiliary pump body roller cavities at intervals along the circumferential direction, part of the oil passage short through hole is communicated with the auxiliary pump body roller cavities, and the main pump body roller cavities and the auxiliary pump body roller cavities are configured in a phase-identical mode;
a roller oil suction groove is also formed in one side, close to the roller cavity of the auxiliary pump body, of the roller cavity of the main pump body, and the roller cavity of the main pump body and the roller cavity of the auxiliary pump body are communicated with the roller oil suction groove; the upper end and the lower end in the roller cavity of the main pump body are provided with axial roller moving grooves; the wall surface of the inner cylinder of the main pump body is circumferentially provided with a plurality of oil duct inner holes which are uniformly distributed at intervals with the oil duct long through holes, and the roller oil suction groove is communicated with the oil duct inner holes;
the cylindrical rollers are installed in the roller cavity of the main pump body and the roller cavity of the auxiliary pump body in pairs, each cylindrical roller comprises a cylindrical rolling ring and a bearing, and the cylindrical rolling rings are matched with the tracks of the pump core assemblies; a roller shaft is arranged in a cylindrical rolling ring of a cylindrical roller arranged in a roller cavity of the auxiliary pump body, a ball head roller shaft is arranged in the cylindrical rolling ring of the cylindrical roller arranged in the roller cavity of the main pump body, the ball head roller shaft can axially move along a roller moving groove and is axially constrained by a track which is close to the adjacent cylindrical roller and the pump core assembly;
the axial lead of the spline shaft is superposed with the axial leads of the auxiliary pump body and the main pump body, the spline shaft is divided into a cylindrical section and a cross shaft section, wherein the cylindrical section is penetrated through the end cover, two groups of axial flanges with phase difference are arranged on the cross shaft section, and a sliding groove is formed between the adjacent axial flanges;
the pump core assembly comprises a piston ring assembly and a concentric ring assembly, the piston ring assembly comprises a group of piston ring long keys, piston rings are sleeved on the outer sides of the piston ring long keys, and the left end and the right end of each piston ring long key are coaxially provided with a piston ring inner rail and a piston ring outer rail through a clamping groove and a step respectively and are fixedly connected through bolts; the long keys of a group of piston rings are symmetrically arranged in the sliding grooves of the cross shaft section and can axially slide along the spline shaft; a plurality of left U-shaped distribution grooves and a plurality of right U-shaped distribution grooves with opposite opening directions are uniformly distributed on the surface of the piston ring at intervals, the groove widths and the interval distances are equal, and the groove widths and the interval distances are matched with the inner hole of the oil duct of the main pump body and the inner diameter of the long through hole of the oil duct;
the projections of the inner track and the outer track of the piston ring in the axial lead direction are in a ring shape, and the inner diameter of the outer track of the piston ring is larger than the outer diameter of the inner track of the piston ring; the opposite axial end surfaces of the piston ring inner track and the piston ring outer track are respectively provided with a cam profile curved surface, and the projection of the cam profile curved surface along the axial direction of the cam is in a ring shape and is provided with axial periodic fluctuation; the cam profile curved surfaces of the piston ring inner track and the piston ring outer track are oppositely arranged in a half-cycle phase difference mode, namely the highest point of the piston ring inner track curved surface axially corresponds to the lowest point of the piston ring outer track curved surface;
the concentric ring assembly comprises a group of concentric ring long keys, the left ends of the concentric ring long keys are provided with a first concentric ring and a concentric ring outer track, and the right ends of the concentric ring long keys are provided with a second concentric ring and a concentric ring inner track; the concentric ring long keys are symmetrically arranged in the sliding grooves of the cross shaft section and can axially slide along the spline shaft; the projections in the axial lead direction of the inner track of the concentric ring and the outer track of the concentric ring are circular rings, and the outer diameter of the outer track of the concentric ring is larger than the inner diameter of the inner track of the concentric ring; the opposite axial end surfaces of the concentric ring inner track and the concentric ring outer track are respectively provided with a cam profile curved surface, and the projection of the cam profile curved surface along the axial lead direction is in a circular ring shape and is provided with axial periodic fluctuation; the cam profile curved surface of the concentric ring inner track and the cam profile curved surface of the concentric ring outer track are oppositely arranged in a half-cycle phase difference manner, namely the highest point of the curved surface of the concentric ring inner track axially corresponds to the lowest point of the curved surface of the concentric ring outer track;
the piston ring assembly and the concentric ring assembly are coaxially and oppositely nested on the spline shaft, and ball rows are arranged between the piston ring long key and the axial flange and between the concentric ring long key and the axial flange; the outer track of the concentric ring is sleeved on the outer side of the inner track of the piston ring, and the outer track of the piston ring is sleeved on the outer side of the inner track of the concentric ring; the highest point of the curved surface of the outer track of the piston ring axially corresponds to the highest point of the curved surface of the outer track of the concentric ring; the piston ring assembly and the concentric ring assembly rotate along with the spline shaft, and simultaneously carry out axial reciprocating motion under the constraint of the cylindrical roller, and the directions are opposite;
the number of the cam profile curved surface, the number of the oil passage short through holes, the number of the oil passage long through holes, the number of the main pump body roller cavities, the number of the auxiliary pump body roller cavities, the number of the oil passage inner holes, the number of the left U-shaped distribution grooves and the number of the right U-shaped distribution grooves are equal;
a left closed cavity is formed by the piston ring, the first concentric ring and the main pump body in a surrounding manner, and a right closed cavity is formed by the piston ring, the second concentric ring and the main pump body in a surrounding manner; the piston ring, the first concentric ring, the second concentric ring and the main pump body are in clearance fit; the annular groove of the main pump body is communicated with the left closed cavity and the right closed cavity through the long oil passage through hole, the annular groove of the auxiliary pump body is communicated with the inner cavity of the pump body through the short oil passage through hole, oil is filled in the inner cavity of the pump body, and the inner cavity of the pump body is communicated with the left closed cavity and the right closed cavity through the inner hole of the oil passage;
when the pump core assembly rotates around the axis, the volumes of the left closed cavity and the right closed cavity are periodically changed along with the reciprocating motion of the piston ring assembly and the concentric ring assembly in opposite directions, and are communicated with the oil duct long through hole and the oil duct inner hole in sequence to continuously suck oil from the annular groove of the auxiliary pump body and discharge the oil to the annular groove of the main pump body.
Further, a sealing ring is arranged between the end cover and the auxiliary pump body, a spline hole is formed in the end face of the spline shaft cylindrical section, and the end cover is fixed to the spline shaft cylindrical section through a step and a retaining ring and is sealed through a U-shaped sealing ring.
Furthermore, the main pump body and the auxiliary pump body are mutually embedded and connected through a stud.
Further, the cam profile curved surface is an equal-adding deceleration cam profile curved surface.
Further, the number of the cam profile curved surface, the number of the oil passage short through holes, the number of the oil passage long through holes, the number of the main pump body roller cavities, the number of the auxiliary pump body roller cavities, the number of the oil passage inner holes, the number of the left U-shaped distribution grooves and the number of the right U-shaped distribution grooves are all 5.
The invention has the beneficial effects that:
1) the displacement is increased. By increasing the number of the cylindrical rollers, the oil suction and drainage times of the working cavity in unit time are greatly increased. The piston ring assembly and the concentric ring assembly simultaneously carry out axial reciprocating motion in opposite directions, and the maximum axial change distance of the working cavity reaches twice of the equal-plus-equal deceleration cam track stroke. Therefore, under the condition of the same external dimension, the structure of the invention is more compact and the discharge capacity is larger.
2) The suction characteristics are improved. The paired cylindrical rollers rotate in opposite directions at high speed in the asymmetrical roller cavities, so that the suction characteristic is improved, the self-pressurization effect is generated, the dynamic pressure support is realized, and the abrasion of the rollers is reduced.
3) The service life is increased. The monoblock pump has a simple structure, the sliding friction pair is greatly reduced, and the transmission part is soaked in oil, so that the lubrication and the cooling are facilitated, and the abrasion is reduced. The cylindrical roller on one side can axially move, and the axial compensation of the abrasion of the rail and the roller is realized.
4) And the modularization of the hydraulic pump is easy to realize by matching with the pump shell. Convenient to overhaul, replace and combine, further increases complete machine life and fortune dimension cost.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a schematic structural view of the auxiliary pump body and the main pump body.
Figure 3a is an exploded view of a piston ring assembly.
Figure 3b is an exploded view of a concentric ring assembly.
Fig. 4a is a schematic view of the structure of a cylindrical roller mounted in a roller cavity of a main pump body.
FIG. 4b is a schematic view of the structure of the cylindrical roller mounted in the roller cavity of the auxiliary pump body.
Fig. 5 is a schematic view of the structure of the ball row and the spline shaft.
Fig. 6a-6e are schematic diagrams illustrating the operation of one cycle of an exemplary rotation of the present invention.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are only some embodiments, but not all embodiments, of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that the orientations or positional relationships indicated as the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., appear based on the orientations or positional relationships shown in the drawings only for the convenience of describing the present invention and simplifying the description, but not for indicating or implying that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" as appearing herein are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly stated or limited, the terms "mounted," "connected," and "connected" should be interpreted broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to the attached drawings, the stacked column type two-dimensional piston monoblock pump comprises an end cover 3, an auxiliary pump body 5 and a main pump body 6 which are sequentially and coaxially arranged along an axial lead, wherein the end cover 3 is fixedly installed on the left end face of the auxiliary pump body 5, the right end of the auxiliary pump body 5 is mutually embedded with the left end of the main pump body 6 and is fixedly connected with the auxiliary pump body 5 through a stud, the end cover 3, the main pump body 6 and the auxiliary pump body 5 jointly enclose a pump body inner cavity, and the pump body inner cavity is provided with a spline shaft 1, a ball row 2, a pump core assembly 4 and a; a sealing ring is arranged between the end cover 3 and the auxiliary pump body 5, a spline hole is formed in the end face of the cylindrical section of the spline shaft 1, and the end cover 3 is fixed to the cylindrical section of the spline shaft 1 through a step and a retaining ring and is sealed through a U-shaped sealing ring.
Defining one end of the end cover 3 as a left end, wherein the axial direction is the direction of the central shaft or the direction parallel to the central shaft, the circumferential direction surrounds the central shaft, the inner side is the direction close to the shaft axis, and the outer side is the direction far away from the shaft axis;
the main pump body 6 is of a double-layer cylindrical structure and comprises an inner cylinder and an outer cylinder which are sequentially sleeved from inside to outside, a part of the left end of the inner cylinder is exposed out of the outer cylinder and extends into the auxiliary pump body 5, a first annular ring is connected between the right end of the inner cylinder and the outer cylinder, and the inner cylinder, the first annular ring and the outer cylinder are connected into a whole; 5 oil passage long through holes A5 for oil discharge are uniformly distributed on the wall surface of the main pump body 6 along the circumferential direction of the position corresponding to the first annular ring, and the oil passage long through holes A5 obliquely penetrate through the outer cylinder and the first annular ring to the middle part of the inner cylinder; the outer wall surface of the main pump body 6 is circumferentially provided with a main pump body annular groove A6 along the position corresponding to the oil passage long through hole A5, and the oil passage long through hole A5 is communicated with the main pump body annular groove A6;
the auxiliary pump body 5 is of a single-layer cylindrical structure, a second annular ring is arranged between the auxiliary pump body 5 and the left end of the inner cylinder, and the auxiliary pump body 5 and the second annular ring are connected into a whole; the wall surface of the auxiliary pump body 5 is circumferentially and uniformly provided with 5 oil duct short through holes A7 for absorbing oil, the oil duct short through hole A7 is positioned at a position close to the left end of the second annular ring, the outer wall surface of the auxiliary pump body 5 is circumferentially provided with an auxiliary pump annular groove A9 at a position corresponding to the oil duct short through hole A7, and the oil duct short through hole A7 is communicated with the auxiliary pump annular groove A9; the first annular ring is provided with 5 main pump body roller cavities A1 at intervals along the circumferential direction, the second annular ring is provided with 5 auxiliary pump body roller cavities A8 at intervals along the circumferential direction, part of the oil passage short through hole A7 is communicated with the auxiliary pump body roller cavity A8, and the main pump body roller cavity A1 and the auxiliary pump body roller cavity A8 are configured in the same phase mode;
a roller oil suction groove A3 is further formed in one side, close to the auxiliary pump body roller cavity A8, of the main pump body roller cavity A1, and the main pump body roller cavity A1 and the auxiliary pump body roller cavity A8 are communicated with the roller oil suction groove A3; the upper end and the lower end in the main pump body roller cavity A1 are provided with axial roller moving grooves A2; the wall surface of the inner cylinder of the main pump body 6 is provided with 5 oil passage inner holes A4 which are uniformly distributed at intervals with the oil passage long through hole A5 along the circumferential direction, and the roller oil suction groove A3 is communicated with the oil passage inner holes A4;
the cylindrical rollers 7 are installed in a main pump body roller cavity A1 and an auxiliary pump body roller cavity A8 in pairs, each cylindrical roller 7 comprises a cylindrical rolling ring 41 and a bearing 42, and the cylindrical rolling rings 41 are matched with the tracks of the pump core assemblies 4; a roller shaft 44 is arranged in the cylindrical rolling ring 41 of the cylindrical roller 7 arranged in the auxiliary pump body roller cavity A8, a ball head roller shaft 43 is arranged in the cylindrical rolling ring 41 of the cylindrical roller 7 arranged in the main pump body roller cavity A1, the ball head roller shaft 43 can axially move along a roller moving groove A2 and is axially restrained by abutting against the adjacent cylindrical roller 7 and a track of the pump core assembly 4;
the axial lead of the spline shaft 1 is superposed with the axial leads of the auxiliary pump body 5 and the main pump body 6, the spline shaft 1 is divided into a cylindrical section and a cross shaft section, wherein the cylindrical section is penetrated through the end cover 3, two groups of axial flanges with 90-degree phase difference are arranged on the cross shaft section, and a sliding groove is formed between the adjacent axial flanges;
the pump core assembly 4 comprises a piston ring assembly and a concentric ring assembly, the piston ring assembly comprises a group of piston ring long keys 32, piston rings 33 are sleeved outside the piston ring long keys 32, and the left end and the right end of the piston ring long keys 32 are respectively provided with a piston ring inner rail 31 and a piston ring outer rail 34 coaxially through a clamping groove and a step and fixedly connected through bolts; a group of piston ring long keys 32 are symmetrically arranged in the sliding groove of the cross shaft section and can axially slide along the spline shaft 1; the surface of the piston ring 33 is evenly provided with 5 left U-shaped flow distribution grooves A10a and 5 right U-shaped flow distribution grooves A10b which have opposite opening directions at intervals, the groove width is equal to the interval distance, and the groove width is matched with the inner diameters of an oil passage inner hole A4 and an oil passage long through hole A5 of the main pump body 6;
the projections of the piston ring inner track 31 and the piston ring outer track 34 in the axial lead direction are annular, and the inner diameter of the piston ring outer track 34 is larger than the outer diameter of the piston ring inner track 31; the opposite axial end surfaces of the piston ring inner track 31 and the piston ring outer track 34 are respectively provided with a cam profile curved surface which is an equal-adding and equal-decelerating cam profile curved surface with 5 periods; the cam profile curved surfaces of the piston ring inner track 31 and the piston ring outer track 34 are oppositely arranged in a half-cycle phase difference mode, namely the highest point of the curved surface of the piston ring inner track 31 axially corresponds to the lowest point of the curved surface of the piston ring outer track 34;
the concentric ring assembly comprises a group of concentric ring long keys 37, a first concentric ring 36 and a concentric ring outer track 35 are arranged at the left end of each concentric ring long key 37, and a second concentric ring 38 and a concentric ring inner track 39 are arranged at the right end of each concentric ring long key 37; a group of concentric ring long keys 37 which are symmetrically arranged in the sliding grooves of the cross shaft section and can slide along the axial direction of the spline shaft 1; the projections of the concentric ring inner rail 39 and the concentric ring outer rail 35 in the axial lead direction are circular rings, and the outer diameter of the concentric ring outer rail 35 is larger than the inner diameter of the concentric ring inner rail 39; the opposite axial end surfaces of the concentric ring inner track 39 and the concentric ring outer track 35 are respectively provided with a cam profile curved surface which is an equal-acceleration and equal-deceleration cam profile curved surface with 5 periods; the cam profile curved surface of the concentric ring inner track 39 and the concentric ring outer track 35 are oppositely arranged in a half-cycle phase difference manner, namely, the highest point of the curved surface of the concentric ring inner track 39 axially corresponds to the lowest point of the curved surface of the concentric ring outer track 35;
the piston ring assembly and the concentric ring assembly are coaxially and oppositely nested on the spline shaft 1, and ball rows 2 are arranged between the piston ring long key 32 and the axial flange and between the concentric ring long key 37 and the axial flange; the outer track 35 of the concentric ring is sleeved on the outer side of the inner track 31 of the piston ring, and the outer track 34 of the piston ring is sleeved on the outer side of the inner track 39 of the concentric ring; the highest point of the curved surface of the piston ring outer track 34 axially corresponds to the highest point of the curved surface of the concentric ring outer track 35; the piston ring assembly and the concentric ring assembly 9 rotate along with the spline shaft 1, and simultaneously carry out axial reciprocating motion under the constraint of the cylindrical roller 7, and the directions are opposite;
a left closed cavity A11 is defined among the piston ring 33, the first concentric ring 36 and the main pump body 6, and a right closed cavity A12 is defined among the piston ring 33, the second concentric ring 38 and the main pump body 6; the piston ring 33, the first concentric ring 36, the second concentric ring 38 and the main pump body 6 are in clearance fit; the annular groove A6 of the main pump body is communicated with a left closed cavity A11 and a right closed cavity A12 through an oil passage long through hole A5, the annular groove A9 of the auxiliary pump body is communicated with an inner cavity of the pump body through an oil passage short through hole A7, oil is filled in the inner cavity of the pump body, and the inner cavity of the pump body is communicated with the left closed cavity A11 and the right closed cavity A12 through an oil passage inner hole A4;
when the pump core assembly 4 rotates around the axis, the volumes of the left closed cavity A11 and the right closed cavity A12 change periodically along with the reciprocating motion of the piston ring assembly 8 and the concentric ring assembly 9 in opposite directions, and are communicated with the oil duct long through hole A5 and the oil duct inner hole A4 in sequence, so that oil is continuously sucked from the annular groove A9 of the auxiliary pump body and is discharged to the annular groove A6 of the main pump body.
The specific working principle is as follows: according to the laminated column type two-dimensional piston monoblock pump, oil is filled in an inner cavity of a pump body from an annular groove A9 through an oil passage short through hole A7, and enters an oil passage inner hole A4 through a roller cavity A1 and a roller cavity A8 which are communicated with a roller oil suction groove A3. The pump core assembly 4 is rotated circumferentially in the direction shown in figure 6a to assume the zero initial position of the moving part as shown in figure 6b, following which the movement of the various assemblies is as shown in figures 6c to 6 e.
As shown in fig. 6b, initially at 0 degree, a first distribution window communicated with the oil passage inner hole a4 by the left U-shaped distribution groove a10a is at an opening threshold, and a second distribution window communicated with the oil passage long through hole a5 by the right U-shaped distribution groove a10b is at an opening threshold. The highest point of the equal-adding equal-deceleration curved surface of the outer track 34 of the piston ring is abutted against the cylindrical roller 7 in the auxiliary pump body 5, and the lowest point of the equal-adding equal-deceleration curved surface of the inner track 39 of the concentric ring is abutted against the cylindrical roller 7 in the auxiliary pump body 5. Meanwhile, the lowest point of the equal deceleration curved surface of the inner track 31 of the piston ring is abutted against the cylindrical roller 7 in the main pump body 6, and the highest point of the equal deceleration curved surface of the outer track 35 of the concentric ring is abutted against the cylindrical roller 7 in the main pump body 6. As the pump core assembly 4 rotates circumferentially, the piston ring assembly 8 begins to move to the right with an equal axial acceleration and the concentric ring assembly 9 begins to move to the left with an equal axial acceleration due to the constraint of the cylindrical roller 7. The first flow distribution window and the second flow distribution window are opened, and the opening degree is gradually increased. The volume of the left closed chamber a11 begins to expand, and oil is sucked from the oil passage inner hole a4 through the first port window. The volume of the right closed cavity A12 begins to shrink, and oil is discharged from the oil passage long through hole A5 through the second distribution window.
As shown in fig. 6c, the pump core assembly 4 rotates circumferentially 18 degrees, the piston ring assembly and the concentric ring assembly reach the middle axial stroke, and the first flow distribution window and the second flow distribution window reach the maximum opening degree. As the pump core assembly 4 continues to rotate, the piston ring assembly 8 starts to continue to move rightwards along the axial equal deceleration, the concentric ring assembly 9 starts to continue to move leftwards along the axial equal deceleration, the opening degrees of the first flow distribution window and the second flow distribution window are gradually reduced, the volume of the left closed cavity A11 continues to be enlarged and oil is sucked, and the volume of the right closed cavity A12 continues to be reduced and oil is discharged.
As shown in fig. 6d, the pump core assembly 4 rotates circumferentially by 36 degrees, the piston ring assembly and the concentric ring assembly reach the end of the axial stroke moving to the left, the volume of the left closed cavity a11 reaches the maximum, the volume of the right closed cavity a12 reaches the minimum, the first flow distribution window and the second flow distribution window are closed, the oil suction process of the left closed cavity a11 is finished, and the oil discharge process of the right closed cavity a12 is finished. At the moment, a third flow distribution window communicated with the left U-shaped flow distribution groove A10a and the oil passage long through hole A5 is in an opening critical state, and a fourth flow distribution window communicated with the left U-shaped flow distribution groove A10b and the oil passage inner hole A4 is in an opening critical state. The lowest point of the equal-adding equal-deceleration curved surface of the outer track 34 of the piston ring is abutted against the cylindrical roller 7 in the auxiliary pump body 5, and the highest point of the equal-adding equal-deceleration curved surface of the inner track 39 of the concentric ring is abutted against the cylindrical roller 7 in the auxiliary pump body 5. Meanwhile, the highest point of the equal deceleration curved surface of the inner track 31 of the piston ring is abutted against the cylindrical roller 7 in the main pump body 6, and the lowest point of the equal deceleration curved surface of the outer track 35 of the concentric ring is abutted against the cylindrical roller 7 in the main pump body 6. As the pump core assembly 4 continues to rotate circumferentially, the piston ring assembly 8 begins to move axially equi-accelerated to the left and the concentric ring assembly 9 begins to move axially equi-accelerated to the right. And opening the third flow distribution window and the fourth flow distribution window, and gradually increasing the opening degree. The volume of the left closed cavity A11 begins to shrink, and oil is discharged from the oil passage long through hole A5 through the third distribution window. The volume of the right closed cavity A12 begins to expand, and oil is sucked from the oil passage inner hole A4 through the fourth distributing window.
As shown in fig. 6e, the pump core assembly 4 rotates circumferentially by 54 degrees, the piston ring assembly and the concentric ring assembly reach the middle axial stroke, and the third flow distribution window and the fourth flow distribution window reach the maximum opening degree. As the pump core assembly 4 continues to rotate, the piston ring assembly 8 starts to move leftwards continuously along the axial equal deceleration, the concentric ring assembly 9 starts to move rightwards continuously along the axial equal deceleration, the opening degrees of the third flow distribution window and the fourth flow distribution window are gradually reduced, the volume of the left closed cavity A11 continues to be reduced, oil is discharged, and the volume of the right closed cavity A12 continues to be enlarged, and oil is sucked.
When the pump core assembly 4 rotates in the circumferential direction by 72 degrees, the positions and the moving trends of all moving parts are the same as those of the moving parts at the initial 0 degrees, the volume of the left closed cavity A11 is minimum, the third flow distribution window is closed, and the oil discharging process of the left closed cavity A11 is finished. The volume of the right closed cavity A12 reaches the maximum, the fourth distribution window is closed, and the oil suction process of the right closed cavity A12 is finished. Continued rotation of the pump core assembly 4 will begin to repeat the cyclical motion described above.
The pump core assembly 4 rotates 72 degrees, and the left closed cavity A11 and the right closed cavity A12 complete 1 oil suction and discharge process respectively. Thus, taking 5-cycle orbit as an example, the pump core assembly 4 rotates 360 degrees for 1 cycle to complete 10 times of oil sucking and discharging processes.
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. Pile column type two dimension piston monoblock pump, its characterized in that: the pump comprises an end cover (3), an auxiliary pump body (5) and a main pump body (6) which are sequentially and coaxially arranged along an axial lead, wherein the end cover (3) is fixedly arranged on the left end face of the auxiliary pump body (5), the right end of the auxiliary pump body (5) is fixedly connected with the left end of the main pump body (6), the end cover (3), the main pump body (6) and the auxiliary pump body (5) jointly enclose a pump body inner cavity, and the pump body inner cavity is provided with a flower shaft (1), a ball row (2), a pump core assembly (4) and a cylindrical roller (7);
defining one end of the end cover (3) as a left end, wherein the axial direction is the direction of the central shaft or the direction parallel to the central shaft, the circumferential direction surrounds the central shaft, the inner side is the direction close to the shaft axis, and the outer side is the direction far away from the shaft axis;
the main pump body (6) is of a double-layer cylindrical structure and comprises an inner cylinder and an outer cylinder which are sequentially sleeved from inside to outside, a part of the left end of the inner cylinder is exposed out of the outer cylinder and extends into the auxiliary pump body (5), a first annular ring is connected between the right end of the inner cylinder and the outer cylinder, and the inner cylinder, the first annular ring and the outer cylinder are connected into a whole; a plurality of oil passage long through holes (A5) for oil discharge are uniformly distributed on the wall surface of the main pump body (6) along the circumferential direction of the position corresponding to the first annular ring, and the oil passage long through holes (A5) obliquely penetrate through the outer cylinder and the first annular ring to the middle part of the inner cylinder; the outer wall surface of the main pump body (6) is circumferentially provided with a main pump body annular groove (A6) along the position corresponding to the oil passage long through hole (A5), and the oil passage long through hole (A5) is communicated with the main pump body annular groove (A6);
the auxiliary pump body (5) is of a single-layer cylindrical structure, a second annular ring is arranged between the auxiliary pump body (5) and the left end of the inner cylinder, and the auxiliary pump body (5) and the second annular ring are connected into a whole; a plurality of oil duct short through holes (A7) for absorbing oil are uniformly distributed on the wall surface of the auxiliary pump body (5) along the circumferential direction, the oil duct short through holes (A7) are positioned at the position close to the left end of the second annular ring, an auxiliary pump annular groove (A9) is circumferentially arranged on the outer wall surface of the auxiliary pump body (5) along the position corresponding to the oil duct short through holes (A7), and the oil duct short through holes (A7) are communicated with the auxiliary pump annular groove (A9); the first annular ring is provided with a plurality of main pump body roller cavities (A1) at intervals along the circumferential direction, the second annular ring is provided with a plurality of auxiliary pump body roller cavities (A8) at intervals along the circumferential direction, part of the oil passage short through hole (A7) is communicated with the auxiliary pump body roller cavities (A8), and the main pump body roller cavities (A1) and the auxiliary pump body roller cavities (A8) are configured in the same phase mode;
a roller oil suction groove (A3) is also formed in one side, close to the auxiliary pump body roller cavity (A8), of the main pump body roller cavity (A1), and the main pump body roller cavity (A1) and the auxiliary pump body roller cavity (A8) are communicated with the roller oil suction groove (A3); the upper end and the lower end in the roller cavity (A1) of the main pump body are provided with axial roller moving grooves (A2); the wall surface of the inner cylinder of the main pump body (6) is provided with a plurality of oil passage inner holes (A4) which are uniformly distributed at intervals with the oil passage long through hole (A5) along the circumferential direction, and the roller oil suction groove (A3) is communicated with the oil passage inner holes (A4);
the cylindrical rollers (7) are installed in a main pump body roller cavity (A1) and an auxiliary pump body roller cavity (A8) in pairs, each cylindrical roller (7) comprises a cylindrical rolling ring (41) and a bearing (42), and the cylindrical rolling rings (41) are matched with the tracks of the pump core assemblies (4); a roller shaft (44) is arranged in a cylindrical rolling ring (41) of a cylindrical roller (7) arranged in an auxiliary pump body roller cavity (A8), a ball head roller shaft (43) is arranged in the cylindrical rolling ring (41) of the cylindrical roller (7) arranged in a main pump body roller cavity (A1), the ball head roller shaft (43) can axially move along a roller moving groove (A2) and is axially constrained by a track abutting against the adjacent cylindrical roller (7) and a pump core assembly (4);
the axial lead of the spline shaft (1) is superposed with the axial leads of the auxiliary pump body (5) and the main pump body (6), the spline shaft (1) is divided into a cylindrical section and a cross shaft section, wherein the cylindrical section is penetrated through the end cover (3), two groups of axial flanges with 90-degree phase difference are arranged on the cross shaft section, and a sliding groove is formed between the adjacent axial flanges;
the pump core assembly (4) comprises a piston ring assembly and a concentric ring assembly, the piston ring assembly comprises a group of piston ring long keys (32), piston rings (33) are sleeved on the outer sides of the piston ring long keys (32), and the left end and the right end of each piston ring long key (32) are respectively provided with a piston ring inner rail (31) and a piston ring outer rail (34) through a clamping groove and a step in a coaxial mode and are fixedly connected through bolts; a group of piston ring long keys (32) are symmetrically arranged in the sliding groove of the cross shaft section and can axially slide along the spline shaft (1); a plurality of left U-shaped distributing grooves (A10a) and right U-shaped distributing grooves (A10b) with opposite opening directions are uniformly distributed on the surface of the piston ring (33) at intervals, the groove widths and the interval distances are equal, and the groove widths and the interval distances are matched with the inner diameters of an oil passage inner hole (A4) and an oil passage long through hole (A5) of the main pump body (6);
the projections of the piston ring inner track (31) and the piston ring outer track (34) in the axial lead direction are annular, and the inner diameter of the piston ring outer track (34) is larger than the outer diameter of the piston ring inner track (31); the opposite axial end surfaces of the piston ring inner track (31) and the piston ring outer track (34) are respectively provided with a cam profile curved surface, and the projection of the cam profile curved surface along the axial direction of the cam is in a ring shape and is provided with axial periodic fluctuation; the cam profile curved surfaces of the piston ring inner track (31) and the piston ring outer track (34) are oppositely arranged in a half-cycle phase difference mode, namely the highest point of the curved surface of the piston ring inner track (31) axially corresponds to the lowest point of the curved surface of the piston ring outer track (34);
the concentric ring assembly comprises a group of concentric ring long keys (37), a first concentric ring (36) and a concentric ring outer track (35) are arranged at the left end of each concentric ring long key (37), and a second concentric ring (38) and a concentric ring inner track (39) are arranged at the right end of each concentric ring long key (37); a group of concentric ring long keys (37) which are symmetrically arranged in the sliding grooves of the cross shaft section and can axially slide along the spline shaft (1); the projections of the concentric ring inner rail (39) and the concentric ring outer rail (35) in the axial lead direction are circular rings, and the outer diameter of the concentric ring outer rail (35) is larger than the inner diameter of the concentric ring inner rail (39); the opposite axial end surfaces of the concentric ring inner track (39) and the concentric ring outer track (35) are respectively provided with a cam profile curved surface, and the projection of the cam profile curved surface along the axial lead direction is in a circular ring shape and is provided with axial periodic fluctuation; the cam profile curved surfaces of the concentric ring inner track (39) and the concentric ring outer track (35) are oppositely arranged in a half-cycle phase difference manner, namely the highest point of the curved surface of the concentric ring inner track (39) axially corresponds to the lowest point of the curved surface of the concentric ring outer track (35);
the piston ring assembly and the concentric ring assembly are coaxially and oppositely nested on the spline shaft (1), and ball rows (2) are arranged between the piston ring long key (32) and the axial flange and between the concentric ring long key (37) and the axial flange; the outer track (35) of the concentric ring is sleeved on the outer side of the inner track (31) of the piston ring, and the outer track (34) of the piston ring is sleeved on the outer side of the inner track (39) of the concentric ring; the highest point of the curved surface of the piston ring outer track (34) axially corresponds to the highest point of the curved surface of the concentric ring outer track (35); the piston ring assembly and the concentric ring assembly (9) rotate along with the spline shaft (1) and simultaneously carry out axial reciprocating motion under the constraint of the cylindrical roller (7), and the directions are opposite;
the number of the cam profile curved surface period, the oil channel short through hole (A7), the oil channel long through hole (A5), the main pump body roller cavity (A1), the auxiliary pump body roller cavity (A8), the oil channel inner hole (A4), the left U-shaped distributing groove (A10a) and the right U-shaped distributing groove (A10b) is equal;
a left closed cavity (A11) is enclosed among the piston ring (33), the first concentric ring (36) and the main pump body (6), and a right closed cavity (A12) is enclosed among the piston ring (33), the second concentric ring (38) and the main pump body (6); the piston ring (33), the first concentric ring (36), the second concentric ring (38) and the main pump body (6) are in clearance fit; the annular groove (A6) of the main pump body is communicated with the left closed cavity (A11) and the right closed cavity (A12) through an oil passage long through hole (A5), the annular groove (A9) of the auxiliary pump body is communicated with the inner cavity of the pump body through an oil passage short through hole (A7), oil is filled in the inner cavity of the pump body, and the inner cavity of the pump body is communicated with the left closed cavity (A11) and the right closed cavity (A12) through an oil passage inner hole (A4);
when the pump core assembly (4) rotates around the axis, the volume of the left closed cavity (A11) and the volume of the right closed cavity (A12) are periodically changed along with the reciprocating motion of the piston ring assembly (8) and the concentric ring assembly (9) in opposite directions, and the left closed cavity and the right closed cavity are communicated with the oil passage long through hole (A5) and the oil passage inner hole (A4) in sequence, continuously suck oil from the annular groove (A9) of the auxiliary pump body, and discharge the oil to the annular groove (A6) of the main pump body.
2. The stacked two-dimensional piston monoblock pump of claim 1, wherein: and a sealing ring is arranged between the end cover (3) and the auxiliary pump body (5), a spline hole is formed in the end surface of the cylindrical section of the spline shaft (1), and the end cover (3) is fixed on the cylindrical section of the spline shaft (1) through a step and a retaining ring and is sealed through a U-shaped sealing ring.
3. The stacked two-dimensional piston monoblock pump of claim 1, wherein: the main pump body (6) and the auxiliary pump body (5) are mutually embedded and connected through a stud.
4. The stacked two-dimensional piston monoblock pump of claim 1, wherein: the cam profile curved surface is an equal-adding and equal-reducing cam profile curved surface.
5. The stacked two-dimensional piston monoblock pump of claim 1, wherein: the number of the cam profile curved surface period, the oil channel short through hole (A7), the oil channel long through hole (A5), the main pump body roller cavity (A1), the auxiliary pump body roller cavity (A8), the oil channel inner hole (A4), the left U-shaped distributing groove (A10a) and the right U-shaped distributing groove (A10b) is 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011065302.9A CN112065682B (en) | 2020-09-30 | Stacked column type two-dimensional piston monoblock pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011065302.9A CN112065682B (en) | 2020-09-30 | Stacked column type two-dimensional piston monoblock pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112065682A true CN112065682A (en) | 2020-12-11 |
| CN112065682B CN112065682B (en) | 2024-06-07 |
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