CN116104723B - A double row plunger pump - Google Patents
A double row plunger pump Download PDFInfo
- Publication number
- CN116104723B CN116104723B CN202211342587.5A CN202211342587A CN116104723B CN 116104723 B CN116104723 B CN 116104723B CN 202211342587 A CN202211342587 A CN 202211342587A CN 116104723 B CN116104723 B CN 116104723B
- Authority
- CN
- China
- Prior art keywords
- plunger
- hole
- swash plate
- hinge block
- assembly
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 46
- 238000006073 displacement reaction Methods 0.000 abstract description 12
- 238000000034 method Methods 0.000 description 10
- 230000002093 peripheral effect Effects 0.000 description 7
- 238000010521 absorption reaction Methods 0.000 description 6
- 238000007599 discharging Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 3
- 230000000149 penetrating effect Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Classifications
-
- 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
- F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
- F04B3/003—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other
- F04B3/006—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other with rotating cylinder block
-
- 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
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
本发明公开了一种双列柱塞泵，包括依次设置的壳体、斜盘座、第一往复组件、第一柱塞、传动轴组件、缸体、第二柱塞、第二往复组件以及端盖，第一往复组件安装在传动轴组件的第一铰块上、并与推力轴承相接触，第二往复组件安装在传动轴组件的第二铰块上与端盖相接触；第一柱塞的小径球头端与缸体的柱塞孔相配合，第一柱塞的大径球头端安装在第一往复组件的第一球窝内，第二柱塞的小径球头端与缸体的柱塞孔相配合，第二柱塞的大径球头端安装在第二往复组件的第二球窝内，第一柱塞、第二柱塞以及缸体均沿轴向贯穿设有油道，端盖和第二往复组件配合设有用于进排油的配流结构。本装置在不增加柱塞泵径向尺寸条件下可有效增大排量，减少摩擦损失。
The present invention discloses a double-row plunger pump, comprising a casing, a swash plate seat, a first reciprocating assembly, a first plunger, a transmission shaft assembly, a cylinder body, a second plunger, a second reciprocating assembly and an end cover, the first reciprocating assembly is mounted on the first hinge block of the transmission shaft assembly and contacts the thrust bearing, the second reciprocating assembly is mounted on the second hinge block of the transmission shaft assembly and contacts the end cover; the small-diameter ball head end of the first plunger matches the plunger hole of the cylinder body, the large-diameter ball head end of the first plunger is mounted in the first ball socket of the first reciprocating assembly, the small-diameter ball head end of the second plunger matches the plunger hole of the cylinder body, the large-diameter ball head end of the second plunger is mounted in the second ball socket of the second reciprocating assembly, the first plunger, the second plunger and the cylinder body are all provided with oil passages along the axial direction, and the end cover and the second reciprocating assembly are provided with a distribution structure for oil inlet and outlet. The device can effectively increase the displacement and reduce friction loss without increasing the radial size of the plunger pump.
Description
Technical Field
The invention relates to the technical field of hydraulic pumps, in particular to a double-row plunger pump.
Background
In the prior art, the end face flow distribution swash plate type axial plunger pump generally adopts a single-row plunger structure, when the pump works, the cylinder body, the plunger and the sliding shoes are driven by the transmission shaft to move together, the flow distribution window on the end face of the cylinder body is matched with the kidney-shaped flow distribution window of the flow distribution plate to form an oil suction and discharge passage, the plunger axially reciprocates to suck and discharge oil under the action of the swash plate while rotating around the transmission shaft, and the sliding shoes and the end face of the swash plate form contact type sealing to ensure the tightness of an oil suction and discharge cavity. When the pump works, the sliding shoes move at high speed on the inclined disc surface to generate friction, and serious friction exists between the cylinder body and the valve plate in the flow distribution process, so that the efficiency of the pump is reduced to a certain extent. In the case of a certain stroke of reciprocation of the plungers, the larger the number of plungers, the larger the displacement of the pump, however, increasing the number of plungers increases the radial dimension of the pump rapidly.
In summary, how to improve the displacement of the plunger pump and avoid the oversized size and structure of the plunger pump is a problem to be solved by those skilled in the art.
Disclosure of Invention
In view of the above, the present invention aims to provide a double-row plunger pump, which can improve the displacement of the plunger pump and avoid the oversized size and structure of the plunger pump, and the device has the characteristics of large displacement, small friction, high efficiency, etc.
In order to achieve the above object, the present invention provides the following technical solutions:
The double-row plunger pump comprises a shell, a swash plate seat, a first reciprocating assembly, a first plunger, a transmission shaft assembly, a cylinder body, a second plunger, a second reciprocating assembly and an end cover which are sequentially arranged, wherein the shell is connected with the end cover, a cavity is formed in the shell, the swash plate seat is arranged at the bottom of the shell, the transmission shaft assembly is arranged in the cavity, one end of the transmission shaft assembly extends out of the bottom of the shell, the other end of the transmission shaft assembly is arranged in the end cover, the cylinder body is sleeved on the peripheral part of the transmission shaft assembly, the first reciprocating assembly is arranged on a first hinge block of the transmission shaft assembly and is in contact with a thrust bearing of the swash plate seat, and the second reciprocating assembly is arranged on a second hinge block of the transmission shaft assembly and is in contact with the end cover;
The first plunger with the second plunger distributes the both ends of cylinder body, the small diameter ball head end of first plunger with the plunger hole of cylinder body cooperatees, the big diameter ball head end of first plunger is installed in the first ball socket of first reciprocal subassembly, the small diameter ball head end of second plunger with the plunger hole of cylinder body cooperatees, the big diameter ball head end of second plunger is installed in the second ball socket of second reciprocal subassembly, first plunger the second plunger with the cylinder body is all run through along the axial and is equipped with the oil duct, the end cover be equipped with the cooperation of second reciprocal subassembly is advanced the joining in marriage the flow structure of oil extraction, the sloping cam plate seat with the end cover is relative the central plane symmetric distribution of cylinder body.
Preferably, a thrust bearing is arranged on the swash plate seat, and the first reciprocating assembly is mounted on the first hinge block and is in contact with the thrust bearing.
Preferably, the left end of the swash plate seat is a flat end surface which is vertically distributed, the right end of the swash plate seat is an inclined end surface, a round hole which is used for penetrating through the transmission shaft assembly is formed in the center of the flat end surface, a pin hole which is used for fixing the swash plate seat on the shell is formed in the outer side of the round hole, and a round sinking table which is used for installing the thrust bearing is vertically arranged on the inclined end surface.
Preferably, the outer peripheral portion of the propeller shaft assembly is provided with an external spline, the inner peripheral portion of the cylinder body is provided with a spline groove for being engaged with the external spline, and the peripheral portion of the spline groove is uniformly provided with plunger holes for being engaged with the first plunger and the second plunger.
Preferably, the inner wall of the cylinder body is provided with two annular baffle grooves for installing the check ring.
Preferably, the transmission shaft group comprises a rotating shaft, a first hinge block, a second hinge block, cylindrical pins and springs, wherein the first hinge block and the second hinge block are sleeved on the periphery of the rotating shaft, the cylindrical pins are used for fixing the first hinge block and the second hinge block, and the springs are arranged between the first hinge block and the external spline, and between the second hinge block and the external spline;
The first hinge block and the second hinge block are symmetrically distributed relative to the external spline, the outer surface of the first hinge block is spherical and matched with the first reciprocating assembly to form a spherical hinge structure, and the outer surface of the second hinge block is spherical and matched with the second reciprocating assembly to form a spherical hinge structure.
Preferably, the first reciprocating assembly comprises a first swash plate, a first pressure plate and a first screw used for connecting the first swash plate and the first pressure plate, wherein a first spherical hole is arranged in the center of the right end face of the first swash plate, and a plurality of first ball sockets are uniformly distributed on the right end face of the first swash plate along the circumferential direction;
A circular counter bore communicated with the first spherical hole is formed in the center of the left end face of the first swash plate, a plurality of first stepped holes for mounting the first screws are uniformly distributed in the circumferential direction of the circular counter bore, and the first stepped holes are uniformly distributed with the first ball socket at intervals;
the center department of first pressure disk be equipped with the first spherical hole of first spherical hole intercommunication, a plurality of first ball holes of circumference equipartition and first fastening hole of first spherical hole, first ball hole with first ball socket corresponds the intercommunication, first fastening hole with first shoulder hole corresponds the intercommunication.
Preferably, the second reciprocating assembly comprises a second swash plate, a second pressure plate and a second screw for connecting the second swash plate and the second pressure plate, wherein a second spherical hole is arranged in the center of the left end face of the second swash plate, and a plurality of second ball sockets are uniformly distributed on the left end face of the second swash plate along the circumferential direction;
a circular boss is arranged at the center of the right end face of the second swash plate, a plurality of second stepped holes for installing the second screws are uniformly distributed on the right end face of the second swash plate along the circumferential direction, and a plurality of inclined holes communicated with the second ball socket are uniformly distributed along the circumferential direction of the circular boss;
the center department of second pressure disk be equipped with the circular hole of second spherical hole intercommunication, the circumference equipartition in circular hole of second a plurality of second ball holes and second fastening hole, the second ball hole with the second ball socket corresponds the intercommunication, the second fastening hole with the second shoulder hole corresponds the intercommunication.
Preferably, one end of the rotating shaft extending out of the swash plate seat is a first end, one end of the rotating shaft inserted into the end cover is a second end, a first support bearing, a framework sealing piece and a check ring piece are sequentially arranged between the first end and the shell along the axial direction, the end part of the first end is connected with the motor, and a second support bearing is arranged between the second end and the end cover.
Preferably, the right end face of the end cover is of a flange structure, the left end face of the end cover is of an inclined plane, and the flow distribution structure comprises an annular boss, an annular groove, a first waist-shaped groove and a second waist-shaped groove, wherein the annular boss is arranged on the inclined plane in parallel, the annular groove is arranged on the annular boss, the first waist-shaped groove is arranged on the outer side of the annular groove and is used for absorbing oil, and the second waist-shaped groove is distributed corresponding to the first waist-shaped groove and is used for discharging oil.
When the double-row plunger pump provided by the invention is used, the operation of the transmission shaft assembly can be controlled, and the transmission shaft assembly can drive the cylinder body, the first reciprocating assembly, the second reciprocating assembly, the first plunger and the second plunger to rotate together. Wherein the first and second reciprocating members are rotated about the drive shaft assembly while being deflected left and right, thereby reciprocating the first and second plungers within the plunger holes. In the rotation process of the transmission shaft assembly, the second reciprocating assembly drives the second plunger to reciprocate along the axial direction under the action of the inclined plane of the end cover, the plunger inner holes of the first plunger and the second plunger and the plunger hole on the cylinder body form a medium containing cavity, the volume of the containing cavity changes periodically when the device operates, the flow distribution is carried out through the flow distribution structure and the oil duct, the oil duct of the second reciprocating assembly coincides with a window of the flow distribution structure for absorbing oil in the range of the rotation angle of the increasing of the containing cavity so as to form an oil absorption oil path, the oil duct of the second reciprocating assembly coincides with the window of the flow distribution structure for discharging oil in the range of the rotation angle of the decreasing of the containing cavity so as to form an oil discharge oil path, and the oil duct inlet of the second reciprocating assembly cannot overlap with the oil absorption window at the same time, so that the oil absorption is separated from the oil discharge, and the normal oil absorption and oil discharge process of the device is ensured.
The device can realize the axial reciprocating motion of the first plunger and the second plunger through the inclined surface structures on the inclined disc seat and the end cover, thereby completing the oil sucking and discharging operation. Through the mode, the device has the characteristics of large discharge capacity, small friction, high efficiency and the like. In addition, the first plunger and the second plunger of this device all use as the fluid passageway, and not main atress transmission part, can effectively improve the result of use and the life of first plunger and second plunger, and can not lead to the size of plunger pump too big.
In summary, the double-row plunger pump provided by the invention can improve the displacement of the plunger pump and avoid the oversized size and structure of the plunger pump, and has the characteristics of large displacement, small friction, high efficiency and the like.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present invention, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.
FIG. 1 is a cross-sectional view of a dual column plunger pump provided by the present invention;
FIG. 2 is a schematic structural view of a driveshaft assembly;
FIG. 3 is a schematic structural view of a rotating shaft;
FIG. 4 is a schematic view of the structure of a first hinge block;
FIG. 5 is a schematic view of a swash plate seat;
FIG. 6 is a schematic view of the first reciprocating assembly;
FIG. 7 is a schematic view of a first swash plate;
FIG. 8 is a cross-sectional view of FIG. 7;
FIG. 9 is a schematic view of the structure of the first platen;
FIG. 10 is a schematic view of a second reciprocating assembly;
FIG. 11 is a schematic view of a construction of a second swash plate;
FIG. 12 is a cross-sectional view of FIG. 11;
FIG. 13 is a schematic view of the structure of the cylinder;
FIG. 14 is a schematic view of the structure of the first plunger;
FIG. 15 is a schematic structural view of an end cap;
Fig. 16 is a half cross-sectional view of fig. 15.
In fig. 1-16:
1 is a shell, 2 is a swash plate seat, 21 is a round hole, 22 is a round sinking table, 23 is a stud hole, 3 is a thrust bearing, 4 is a first reciprocating assembly, 41 is a first swash plate, 42 is a first platen, 43 is a first screw, 44 is a first ball socket, 45 is a first spherical hole, 46 is a round counter bore, 47 is a first stepped hole, 48 is a first spherical hole, 49 is a first spherical hole, 410 is a first fastening hole, 5 is a first plunger, 6 is a transmission shaft assembly, 61 is a first hinge block, 62 is a second hinge block, 63 is an external spline, 64 is a rotating shaft, 641 is a first support bearing, 642 is a skeleton seal, 643 is a retainer ring member 644 is a second support bearing, 65 is a spring, 66 is a retainer ring, 67 is a cylindrical pin, 7 is a cylinder, 71 is a plunger hole, 72 is a spline groove, 73 is a baffle groove, 8 is a second plunger, 9 is a second reciprocating assembly, 91 is a second swash plate, 92 is a second pressure plate, 93 is a second screw, 94 is a second ball socket, 95 is a second spherical hole, 96 is a circular boss, 97 is a second stepped hole, 98 is an inclined hole, 99 is a second circular hole, 910 is a second spherical hole, 911 is a second fastening hole, 10 is an end cover, 101 is a flow distribution structure, 1011 is an annular boss, 1012 is an annular groove, 1013 is a first waist-shaped groove, 1014 is a second waist-shaped groove.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The invention has the core of providing the double-row plunger pump, which can improve the displacement of the plunger pump and simultaneously avoid the oversized size and structure of the plunger pump, and the device has the characteristics of large displacement, small friction, high efficiency and the like.
Please refer to fig. 1 to 16.
The embodiment provides a double-row plunger pump, which comprises a shell 1, a swash plate seat 2, a first reciprocating assembly 4, a first plunger 5, a transmission shaft assembly 6, a cylinder body 7, a second plunger 8, a second reciprocating assembly 9 and an end cover 10 which are sequentially arranged, wherein the shell 1 is connected with the end cover 10, a cavity is formed in the two, the swash plate seat 2 is arranged at the bottom of the shell 1, the transmission shaft assembly 6 is arranged in the cavity, one end of the transmission shaft assembly 6 extends out from the bottom of the shell 1, the other end of the transmission shaft assembly is arranged in the end cover 10, the cylinder body 7 is sleeved on the periphery of the transmission shaft assembly 6, the first reciprocating assembly 4 is arranged on a first hinge block 61 of the transmission shaft assembly 6 and is in contact with a thrust bearing 3 of the swash plate seat 2, and the second reciprocating assembly 9 is arranged on a second hinge block 62 of the transmission shaft assembly 6 and is in contact with the end cover 10;
the first plunger 5 and the second plunger 8 are distributed at two ends of the cylinder 7, the small-diameter ball head end of the first plunger 5 is matched with the plunger hole 71 of the cylinder 7, the large-diameter ball head end of the first plunger 5 is installed in the first ball socket 44 of the first reciprocating assembly 4, the small-diameter ball head end of the second plunger 8 is matched with the plunger hole 71 of the cylinder 7, the large-diameter ball head end of the second plunger 8 is installed in the second ball socket 94 of the second reciprocating assembly 9, oil ducts are formed in the first plunger 5, the second plunger 8 and the cylinder 7 in a penetrating mode in the axial direction, the end cover 10 is provided with a flow distribution structure 101 matched with the second reciprocating assembly 9 for oil inflow and drainage, and the swash plate seat 2 and the end cover 10 are symmetrically distributed relative to the central surface of the cylinder 7.
It should be noted that, the first plunger 5 and the second plunger 8 may be configured as rod-shaped structures, and two ends of the rod-shaped structures have ball structures with different diameters, an oil duct (a tapered through hole) is provided in the middle of the rod-shaped structures, a large orifice of the tapered through hole is located at a large-diameter ball end of the plunger, and a small orifice of the tapered through hole is located at a small-diameter ball end of the plunger. The shape, structure, size, material, position and the like of the casing 1, the swash plate seat 2, the first reciprocating assembly 4, the first plunger 5, the transmission shaft assembly 6, the cylinder block 7, the second plunger 8, the second reciprocating assembly 9 and the end cover 10 can be determined according to actual conditions and actual demands in the actual application process.
When the double-row plunger pump provided by the invention is used, the operation of the transmission shaft assembly 6 can be controlled, and the transmission shaft assembly 6 can drive the cylinder body 7, the first reciprocating assembly 4, the second reciprocating assembly 9, the first plunger 5 and the second plunger 8 to rotate together. Wherein the first and second reciprocating members 4 and 9 are rotated about the driving shaft assembly 6 while being biased left and right, thereby reciprocating the first and second plungers 5 and 8 within the plunger holes 71. In the rotation process of the transmission shaft assembly 6, the second reciprocating assembly 9 drives the second plunger 8 to reciprocate along the axial direction under the action of the inclined surface of the end cover 10, the plunger inner holes of the first plunger 5 and the second plunger 8 and the plunger hole 71 on the cylinder 7 form a medium containing cavity, the volume of the containing cavity changes periodically when the device operates, the flow distribution is carried out through the flow distribution structure 101 and the oil duct, in the range of the increased rotation angle of the containing cavity, the oil duct of the second reciprocating assembly 9 coincides with the window of the flow distribution structure 101 for absorbing oil to form an oil absorption oil duct, in the range of the reduced rotation angle of the containing cavity, the oil duct of the second reciprocating assembly 9 coincides with the window of the flow distribution structure 101 for discharging oil to form an oil discharge oil duct, and the oil duct inlet of the second reciprocating assembly 9 does not overlap with the oil suction window at the same time, so that the oil absorption is separated from the oil discharge, and the normal oil suction and discharge process of the device is ensured.
That is, the device can realize the axial reciprocating motion of the first plunger 5 and the second plunger 8 through the inclined structures on the inclined disc seat 2 and the end cover 10, thereby completing the oil sucking and discharging operation. Through the mode, the device has the characteristics of large discharge capacity, small friction, high efficiency and the like. In addition, the first plunger 5 and the second plunger 8 of the device are used as oil liquid channels, and are not main stress transmission components, so that the use effect and the service life of the first plunger 5 and the second plunger 8 can be effectively improved, and the size of a plunger pump cannot be excessively large.
In summary, the double-row plunger pump provided by the invention can improve the displacement of the plunger pump and avoid the oversized size and structure of the plunger pump, and has the characteristics of large displacement, small friction, high efficiency and the like.
On the basis of the above embodiment, it is preferable that the swash plate base 2 is provided with a thrust bearing 3, and the first reciprocating assembly 4 is mounted on the first hinge block 61 and contacts the thrust bearing 3. The first reciprocating assembly 4 and the second reciprocating assembly 9 can be respectively positioned at the left side and the right side of the cylinder 7, the first plunger 5 and the second plunger 8 are respectively positioned at two ends of the cylinder 7, namely one end of the plunger is matched with the reciprocating assembly, the other end of the plunger is matched with the cylinder 7, the first reciprocating assembly 4 is contacted with the thrust bearing 3, and the second reciprocating assembly 9 is contacted with the inclined surface structure of the end cover 10. By arranging the thrust bearing 3, the transmission connection effect between the swash plate seat 2 and the first reciprocating assembly 4 can be effectively improved, and serious abrasion between the swash plate seat 2 and the first reciprocating assembly 4 is avoided.
Preferably, the left end of the swash plate seat 2 is a flat end surface which is vertically distributed, the right end of the swash plate seat 2 is an inclined end surface, a round hole 21 which is used for penetrating through the transmission shaft assembly 6 is formed in the center of the flat end surface, a pin hole 23 which is used for fixing the swash plate seat 2 on the shell 1 is formed in the outer side of the round hole 21, a round sinking table 22 which is used for installing the thrust bearing 3 is vertically arranged on the inclined end surface, and the structure is shown in the figure. A certain included angle exists between the flat end face and the inclined end face, the flat end is provided with a stud hole 23, the inclined end face is provided with a circular sinking table 22 along the normal direction of the inclined end face, and the bottom surface of the circular sinking table 22 is parallel to the inclined end face so as to facilitate the installation of the thrust bearing 3.
Preferably, the outer peripheral portion of the drive shaft assembly 6 is provided with an external spline 63, the inner peripheral portion of the cylinder 7 is provided with a spline groove 72 for engagement with the external spline 63, and the peripheral portion of the spline groove 72 is uniformly provided with plunger holes 71 for engagement with the first plunger 5 and the second plunger 8. An assembly hole may be provided on both sides of the external spline 63, and the assembly hole is used for installing a connecting pin, so as to ensure the assembly effect of the external spline 63 and the spline groove 72, and further ensure the connection effect of the transmission shaft assembly 6 and the cylinder 7. Further, the plurality of plunger holes 71 are uniformly distributed in the circumferential portion of the spline groove 72, so that the first plunger 5 and the second plunger 8 can be uniformly distributed in the circumferential portion of the cylinder 7, and the force applied to the cylinder 7 can be balanced.
Preferably, the inner wall of the cylinder 7 is provided with two annular retaining grooves 73 for mounting the retaining ring 66. The retainer ring 66 is installed in the baffle slot 73, and can axially limit the cylinder body 7, so that axial movement of the cylinder body 7 is avoided, and the cylinder body 7 only circumferentially rotates along with the transmission shaft assembly 6.
Preferably, the transmission shaft group comprises a rotating shaft 64, a first hinge block 61 and a second hinge block 62 sleeved on the periphery of the rotating shaft 64, a cylindrical pin 67 for fixing the first hinge block 61 and the second hinge block 62 and a spring 65, wherein the spring 65 is arranged between the first hinge block 61 and the external spline 63 and between the second hinge block 62 and the external spline 63; the first hinge block 61 and the second hinge block 62 are symmetrically distributed relative to the external spline 63, the outer surface of the first hinge block 61 is spherical and matched with the first reciprocating assembly 4 to form a spherical hinge structure, and the outer surface of the second hinge block 62 is spherical and matched with the second reciprocating assembly 9 to form a spherical hinge structure.
It should be noted that, the outer surfaces of the first hinge block 61 and the second hinge block 62 are spherical, and the first hinge block 61 and the second hinge block 62 are provided with through holes for passing through the rotating shaft 64 along the axial direction, and the first hinge block 61 and the second hinge block 62 are provided with fixing holes for passing through the cylindrical pins 67 along the radial direction, so as to ensure that the first hinge block 61 and the second hinge block 62 can rotate along the circumferential direction of the rotating shaft 64 and cannot axially float. The spherical surfaces of the first hinge block 61 and the first reciprocating assembly 4 are matched to form a spherical hinge structure, and the spherical surfaces of the second hinge block 62 and the second reciprocating assembly 9 are matched to form a spherical hinge structure. The springs 65 are arranged between the end face of the first hinge block 61 and the end face of the external spline 63 and between the end face of the second hinge block 62 and the end face of the external spline 63, so that the first hinge block 61 and the second hinge block 62 can effectively bear axial acting force, and therefore, the first reciprocating assembly 4 and the second reciprocating assembly 9 respectively generate left and right deflection around the first hinge block 61 and the second hinge block 62 while the first reciprocating assembly 4 and the second reciprocating assembly 9 rotate around the shaft, and at the same time, the first plunger 5 and the second plunger 8 can reciprocate in the plunger hole 71.
On the basis of the above embodiment, it is preferable that the first reciprocating assembly 4 includes a first swash plate 41, a first pressure plate 42, and a first screw 43 for connecting the first swash plate 41 and the first pressure plate 42, a first spherical hole 45 is provided at the center of the right end surface of the first swash plate 41, and a plurality of first ball sockets 44 are uniformly distributed on the right end surface of the first swash plate 41 in the circumferential direction; a circular counter bore 46 communicated with the first spherical hole 45 is arranged in the center of the left end face of the first swash plate 41, a plurality of first stepped holes 47 for installing the first screws 43 are uniformly distributed in the circumferential direction of the circular counter bore 46, and the first stepped holes 47 are uniformly distributed with the first ball sockets 44 at intervals; the center of the first pressure plate 42 is provided with a first spherical hole 48 communicated with the first spherical hole 45, a plurality of first spherical holes 49 and first fastening holes 410 are uniformly distributed in the circumferential direction of the first spherical hole 48, the first spherical holes 49 are correspondingly communicated with the first ball socket 44, and the first fastening holes 410 and the first stepped holes 47 are correspondingly communicated.
Therefore, the end face of the first ball socket 44 on the first swash plate 41 contacts with the end face of the first ball hole 49 on the first pressure plate 42, the first ball socket 44 and the end face of the first ball hole are matched to accommodate the large-diameter ball end of the first plunger 5, and the first swash plate 41 and the first pressure plate 42 can be connected through the first screw 43, so that synchronous rotation of the first ball socket and the first pressure plate is achieved. In addition, slots may be symmetrically formed in the wall of the first spherical hole 45 so that pins on the rotation shaft 64 are inserted into the first swash plate 41 to rotate the first swash plate 41.
Preferably, the second reciprocating assembly 9 comprises a second swash plate 91, a second pressure plate 92 and a second screw 93 for connecting the second swash plate 91 and the second pressure plate 92, wherein a second spherical hole 95 is arranged at the center of the left end face of the second swash plate 91, and a plurality of second ball sockets 94 are uniformly distributed on the left end face of the second swash plate 91 along the circumferential direction; a circular boss 96 is arranged at the center of the right end surface of the second swash plate 91, a plurality of second stepped holes 97 for installing second screws 93 are uniformly distributed on the right end surface of the second swash plate 91 along the circumferential direction, and a plurality of inclined holes 98 communicated with the second ball socket 94 are uniformly distributed along the circumferential direction of the circular boss 96; the center of the second pressing plate 92 is provided with a second circular hole 99 communicated with the second spherical hole 95, a plurality of second spherical holes 910 and second fastening holes 911 are uniformly distributed in the circumferential direction of the second circular hole 99, the second spherical holes 910 are correspondingly communicated with the second ball sockets 94, and the second fastening holes 911 and the second stepped holes 97 are correspondingly communicated.
That is, the second swash plate 91 has a circular boss 96 added to the end surface of the second swash plate 91 on the basis of the first swash plate 41, and a petal-shaped groove may be provided in the middle of the circular boss 96, and inclined holes 98 communicating with the second ball socket 94 are uniformly distributed in the circumferential direction of the petal-shaped groove, and the inclined holes 98 may be selectively communicated with a flow distribution structure 101 on the end cover 10 to perform oil suction or oil discharge operation. The end face of the second ball hole 910 is correspondingly communicated with and contacted with the end face of the second ball socket 94, the end face of the second ball hole and the end face of the second ball socket are matched to accommodate the large-diameter ball head end of the second plunger 8, and the second swash plate 91 and the second pressure plate 92 can be connected through the second screw 93, so that synchronous rotation of the second swash plate 91 and the second pressure plate is realized. In addition, slots may be symmetrically formed in the wall of the second spherical hole 95 so that pins on the rotation shaft 64 are inserted into the second swash plate 91 to rotate the second swash plate 91.
Preferably, one end of the rotating shaft 64 extending out of the swash plate seat 2 is a first end, one end of the rotating shaft 64 inserted into the end cover 10 is a second end, and a first support bearing 641, a framework seal 642 and a retainer 643 are sequentially arranged between the first end and the housing 1 along the axial direction, so as to ensure sealing connection between the rotating shaft 64 and the housing 1 and smooth rotation of the rotating shaft 64 relative to the housing 1. The end of the first end is connected to the motor and the shaft 64 is driven to rotate synchronously with the motor output shaft by controlling the motor to operate. A second support bearing 644 is provided between the second end and the end cap 10, for example, a blind hole for mounting the second support bearing 644 may be provided in the axial direction of the end cap 10 to prevent the second end and the end cap 10 from being worn out and ensure smooth rotation of the rotary shaft 64.
Preferably, the right end face of the end cover 10 is a flange structure, the left end face of the end cover 10 is an inclined plane, and the flow distribution structure 101 comprises an annular boss 1011 arranged on the inclined plane in parallel, an annular groove 1012 arranged on the annular boss 1011, a first waist-shaped groove 1013 arranged outside the annular groove 1012 and used for absorbing oil, and a second waist-shaped groove 1014 distributed corresponding to the first waist-shaped groove 1013 and used for discharging oil.
It should be noted that, the included angle between the right end face and the left end face of the end cover 10 is equal to the included angle between the two end faces of the swash plate seat 2, the inclined plane is provided with an annular boss 1011, the annular boss 1011 is parallel to the inclined plane, the annular boss 1011 is provided with a circle of annular grooves 1012, the outer side of the annular grooves 1012 is provided with two sections of waist grooves, the pump plays a role in flow distribution during operation, the flow communication of the oil suction oil path and the oil discharge oil path is ensured, and meanwhile, the mutual separation of the oil suction and discharge paths is ensured. The device increases the number of the plungers by symmetrically distributing the plungers on the left side and the right side of the cylinder body 7 so as to effectively improve the displacement of the pump. Moreover, by adding an inclined plane on the end cover 10 and forming a kidney-shaped groove, oil distribution of the double-row plunger pump is realized, and meanwhile, the friction pair of the pump is reduced by introducing the thrust bearing 3, so that friction is effectively reduced, the working efficiency of the pump is improved, and the service life of the pump is prolonged.
In order to further explain the use method of the double-row plunger pump provided by the invention, an example is given below.
When the pump works, the transmission shaft assembly 6 drives the cylinder body 7, the first reciprocating assembly 4, the second reciprocating assembly 9, the first plunger 5 and the second plunger 8 to rotate together, on one hand, the first reciprocating assembly 4 and the first hinge block 61 form a spherical hinge structure, on the other hand, the central line of the contact surface of the first reciprocating assembly 4 and the thrust bearing 3 is intersected with the axis of the rotating shaft 64, the intersection point is overlapped with the spherical center of the spherical surface of the first hinge block 61, so that the first reciprocating assembly 4 rotates around the rotating shaft 64 and simultaneously generates left-right deflection, the first plunger 5 reciprocates in the plunger hole 71, and the second plunger 8 is driven to reciprocate along the axial direction by the second swash plate 91 under the action of the inclined surface structure of the end cover 10 in the rotating process of the rotating shaft 64. The plunger inner hole (oil passage) of the second plunger 8 and the plunger hole 71 on the cylinder 7 form a medium containing cavity, the volume of the containing cavity changes periodically when the pump works, and the pump distributes flow with the flow distribution structure 101 on the end cover 10 through the inclined hole 98 on the end surface of the second swash plate 91.
For example, in the angular range where the cavity increases, the inclined hole 98 of the end surface of the second swash plate 91 coincides with the first waist-shaped groove 1013 to constitute an oil suction path; in the angular range where the cavity is reduced, the inclined hole 98 of the end face of the second swash plate 91 coincides with the second waist-shaped groove 1014 to constitute an oil discharge path. During operation of the pump, the inclined holes 98 do not overlap the first and second waist-shaped grooves 1013, 1014 at the same time, so that the oil suction operation is separated from the oil discharge operation, and the normal oil suction and discharge process of the pump is ensured.
It should be noted that, in the present document, the first and second cases 1110 and 1120, the first photographing hole 111 and the second photographing hole 131 are mentioned, where the first and second cases are merely for distinguishing the difference of positions, and there is no order of precedence.
It should be noted that the positional or positional relationship indicated by "above", "below", etc. of the present application is based on the positional or positional relationship shown in the drawings, and is merely for convenience of description and understanding, and is not indicative or implying that the apparatus or element in question must have a specific orientation, be configured and operated in a specific orientation, and therefore, the present application should not be construed as being limited thereto.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other. Any combination of all the embodiments provided in the present invention is within the protection scope of the present invention, and will not be described herein.
The double-row plunger pump provided by the invention is described in detail above. The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present invention and its core ideas. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the invention can be made without departing from the principles of the invention and these modifications and adaptations are intended to be within the scope of the invention as defined in the following claims.
Claims (7)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211342587.5A CN116104723B (en) | 2022-10-28 | 2022-10-28 | A double row plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211342587.5A CN116104723B (en) | 2022-10-28 | 2022-10-28 | A double row plunger pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN116104723A CN116104723A (en) | 2023-05-12 |
| CN116104723B true CN116104723B (en) | 2024-11-12 |
Family
ID=86266336
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211342587.5A Active CN116104723B (en) | 2022-10-28 | 2022-10-28 | A double row plunger pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116104723B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110067714A (en) * | 2019-03-13 | 2019-07-30 | 钟彪 | A kind of axial plunger pump or motor |
| CN110067713A (en) * | 2019-03-13 | 2019-07-30 | 钟彪 | A kind of tandem axial plunger pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3807283A (en) * | 1970-05-18 | 1974-04-30 | Cessna Aircraft Co | Axial piston pump or motor |
| CN110067715B (en) * | 2019-03-13 | 2024-06-07 | 上海强田驱动技术有限公司 | Flow distribution slide plate pair and plunger pump or motor comprising same |
| CN114687976A (en) * | 2020-12-31 | 2022-07-01 | 钟彪 | Large-traffic compact electricity liquid all-in-one |
-
2022
- 2022-10-28 CN CN202211342587.5A patent/CN116104723B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110067714A (en) * | 2019-03-13 | 2019-07-30 | 钟彪 | A kind of axial plunger pump or motor |
| CN110067713A (en) * | 2019-03-13 | 2019-07-30 | 钟彪 | A kind of tandem axial plunger pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN116104723A (en) | 2023-05-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110067724B (en) | Slide disk supported through-shaft plunger pump or motor | |
| JP2009529619A (en) | Axial plunger pump or motor | |
| CN109236598B (en) | Plunger pump swash plate valve plate assembly | |
| WO2017015782A1 (en) | Novel axial piston pump | |
| US11661928B2 (en) | Piston pump and piston motor | |
| CN106837725A (en) | Two-dimensional axial plunger displacement pump | |
| CN206562977U (en) | Two-dimensional axial plunger pump | |
| CN107781125B (en) | Float type two dimension double crosslinking piston pump | |
| CN114483512B (en) | Miniature water hydraulic pump | |
| CN210422901U (en) | Low-pulsation axial plunger pump with flow adjustable from zero | |
| CN116104723B (en) | A double row plunger pump | |
| US2385990A (en) | Pump | |
| CN214577560U (en) | Antipollution swash plate type plunger pump | |
| CN112483343A (en) | Low-pulsation axial plunger pump with unidirectional output and adjustable flow from zero | |
| CN216342554U (en) | Inner curve hydraulic motor with bidirectional oil distribution | |
| CN214660670U (en) | Axial plunger pump or motor | |
| JP6733991B2 (en) | Plunger pump and brake device | |
| CN206092303U (en) | floating type two-dimensional duplex piston pump | |
| CN206092302U (en) | Inlet supercharging type two-dimensional duplex piston pump | |
| CN105370526B (en) | Scattered many cup formula symmetric double sloping tray axial plunger piston pumps of center annular disk flow | |
| CN209855979U (en) | Axial plunger pump or motor | |
| CN209761643U (en) | Flow distribution sliding disc pair and plunger pump or motor comprising same | |
| CN108317118B (en) | Buckle type split plunger pump swash plate variable adjusting mechanism and adjusting method | |
| CN110552855A (en) | multilayer radial large-flow high-pressure multi-plunger oil pump device | |
| WO2019196389A1 (en) | Variable displacement pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |