CN103758721A - Axial-flow type hydraulic pump with double rows of radial plungers - Google Patents
Axial-flow type hydraulic pump with double rows of radial plungers Download PDFInfo
- Publication number
- CN103758721A CN103758721A CN201310491946.8A CN201310491946A CN103758721A CN 103758721 A CN103758721 A CN 103758721A CN 201310491946 A CN201310491946 A CN 201310491946A CN 103758721 A CN103758721 A CN 103758721A
- Authority
- CN
- China
- Prior art keywords
- plunger
- axis hole
- pentacle weel
- end cap
- eccentric shaft
- 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.)
- Granted
Links
Images
Landscapes
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention discloses an axial-flow type hydraulic pump with double rows of radial plungers, wherein two rows of plunger groups are arrayed in the pump in parallel, the movements of the plunger groups are not affected by each other, and the space in the pump body is used in the maximum degree. According to the axial-flow type hydraulic pump with double rows of radial plungers, an eccentric shaft drives a star wheel to push the plungers to move, the transmission is realized through rolling friction, so that the axial-flow type hydraulic pump with double rows of radial plungers is simple and reliable; the total output of the pump is the sum of the output abilities of all the plunger groups, so that the delivery capacity is high; a plurality of cylinders work together, so that the output peak values of the cylinders are complementary, and the total flow fluctuation can be lowered obviously; the plungers and the plunger cylinder barrels are independent from the pump body, so that the axial-flow type hydraulic pump with double rows of radial plungers is simple to process, is low in cost, is convenient to assemble and maintain, and can be mounted and demounted quickly; the pump uses axial flow mode, the parts among the plungers, the star wheel, the eccentric shaft, an oil inlet and an oil outlet are sealed, so that the capacity utilization ratio is high.
Description
Technical field
The invention belongs to radial plunger oil hydraulic pump technical field, be specifically related to a kind of axial-flow type biserial radial plunger oil hydraulic pump.
Background technique
Oil hydraulic pump is as the core parts of Hydraulic Power Transmission System, it is the source of hydraulic system power, also be the key link that produces leakage and noise simultaneously, for improve system capacity usage ratio, reduce vibration, one of the most effective way is exactly to develop that volumetric efficiency is high, flow oil hydraulic pump stably.In all kinds of oil hydraulic pumps, radial plunger oil hydraulic pump is widely used in the hydraulic system of all kinds of operations involving high pressures with its wearing and tearing remarkable advantage little, that discharge capacity is large, volumetric efficiency is high, as: die casting, injection moulding, forging and stamping and petroleum production etc.
Traditional radial plunger pump generally adopts crank-link mechanism, drives crank to rotate drive plunger move reciprocatingly in cylinder body by eccentric shaft, common are twin cylinder pump, triplex pump and five cylinder pumps etc.This class pump is structurally difficult to realize the design of a fairly large number of plunger case, thereby the fluctuation of the output flow of pump is larger.In order to reduce flowed fluctuation as far as possible, just need suitably to increase the length of connecting rod in practice, therefore, this type of pump has larger axial volume conventionally.In addition, between each member due to crank-link mechanism, be connected through the hinge, transmission link complexity, and there is dead center position, therefore efficiency is lower.
Summary of the invention
In order to overcome the shortcoming of above-mentioned prior art, the object of the invention is to propose a kind of axial-flow type biserial radial plunger oil hydraulic pump, there is compact structure, transmission is simple, output flow is large, flowed fluctuation is little, be convenient to maintenance and volumetric efficiency high.
In order to achieve the above object, the technological scheme that the present invention takes is:
A kind of axial-flow type biserial radial plunger oil hydraulic pump, comprise the pump housing 27, ten groups of plunger groups 4 are installed altogether on the pump housing 27, ten groups of plunger groups 4 are double-row parallel and arrange, the plunger group 4 of every row is radial and is evenly arranged, every group of plunger group 4 comprises plunger case gland 1, plunger case 2 and plunger 3, plunger case gland 1 is arranged on plunger case 2 bottoms, plunger 3 inserts from the other end of plunger case 2, at the interior straight line motion of plunger case 2, the tapped hole that screw screws on the pump housing 27 through the flange on plunger case gland 1 and plunger case 2 achieves a fixed connection;
Pentacle weel transmission system 19 is also dually arrayed and is arranged on the eccentric part of eccentric shaft 7, and be connected with the plunger group 4 of corresponding position respectively, pentacle weel transmission system 19 comprises pentacle weel 15, the first rolling bearing 13, the second rolling bearing 17, the first pentacle weel end cap 12, the second pentacle weel end cap 18 and the first check ring 14, the second check ring 16 and needle roller 24, eccentric shaft 7 is arranged in the pump housing 27, pentacle weel 15 is arranged on the eccentric part of eccentric shaft 7, by the first rolling bearing 13 and the second rolling bearing 17, support, the first pentacle weel end cap 12 and the second pentacle weel end cap 18 are arranged on respectively pentacle weel 15 both sides, and with bolt, pass pentacle weel 15 and lock, the seam of the first pentacle weel end cap 12 and the second pentacle weel end cap 18 inside is pressed on the bearing outer ring of the first rolling bearing 13 and the second rolling bearing 17, the bearing inner race of the first rolling bearing 13 and the second rolling bearing 17 is pressed in respectively on the first check ring 14 and the second check ring 16 of installing on eccentric shaft 7, on every limit of pentacle weel 15, all have plural axial arc groove, needle roller 24 is installed in each arc groove, needle roller 24 can be in arc groove Free-rolling, on the first pentacle weel end cap 12 and the second pentacle weel end cap 18, there is flange 25, flange 25 is enclosed in all needle rollers 24 in arc groove separately, the backhaul flanging 26 of the first pentacle weel end cap 12 and the second pentacle weel end cap 18 outer rims fastens the square flange of plunger 3 bottoms, plunger 3 is against on needle roller 24, realize being connected of needle roller 24 and plunger 3, pentacle weel Mei Bian center is also separately installed with a pressure ring 28, pressure ring 28 props up plunger 3 bottoms, the oilhole at the center of plunger 3, radial oilhole 33 on oilhole and the pentacle weel 15 at pressure ring 28 centers keeps being communicated with when work,
The first abutment sleeve 11 is all installed on the shaft part at eccentric shaft 7 two ends successively, the 3rd rolling bearing 10, the second abutment sleeve 9 and the 4th rolling bearing 8, eccentric shaft 7 is bearing on the first pump end cap 5 and the second pump end cap 20 by the 3rd rolling bearing 10 and the 4th rolling bearing 8, the first pump end cap 5 and the second pump end cap 20 are arranged on respectively the both sides of the pump housing 27, the first axle head gland 6 is arranged on the first pump end cap 5, seam on the first axle head gland 6 is pushed down the outer ring of the 4th rolling bearing 8 of this side, the outer ring of the 4th rolling bearing 8 of opposite side is compressed by the shoulder of the second pump end cap 20 inside, the second axle head gland 22 is arranged on the second pump end cap 20, axial aperture on eccentric shaft 7 is sealed.
In the eccentric part of eccentric shaft 7, all have symmetrically two arc grooves, wherein the first oil suction groove 29 and the first pressure oil groove 32 are one group and are positioned in same eccentric part, the second oil suction groove 37 and the second pressure oil groove 34 are one group and are positioned in another eccentric part, every group of arc groove is all about the axial plane of symmetry symmetry of eccentric shaft 7, and differ 180 ° between two groups of arc grooves, on eccentric shaft, also have the first oil suction axis hole 30, the first force feed axis hole 31, the second oil suction axis hole 36 and the second force feed axis hole 35, these four axis holes are uniform centered by the center of rotation of eccentric shaft 7, its distribution radius is the half of least radius on eccentric shaft 7, and the first oil suction axis hole 30 and the second oil suction axis hole 36 differ 180 °, the first force feed axis hole 31 and the second force feed axis hole 35 differ 180 °, the first oil suction axis hole 30 and the first force feed axis hole 31 are communicated with by radial hole with the first oil suction groove 29 and the first pressure oil groove 32 respectively, the second oil suction axis hole 36 and the second force feed axis hole 35 are communicated with the second oil suction groove 37 and the second pressure oil groove 34 respectively, one end that eccentric shaft 7 coordinates with the second pump end cap 20, be provided with two annular grooves its partial parallel near axle head, between two annular grooves and on the shaft part of both sides, seal ring is all installed, one of them annular groove is communicated with the first oil suction axis hole 30 and the second oil suction axis hole 36 by radial direction through hole, another annular groove is communicated with the first force feed axis hole 31 and the second force feed axis hole 35 by radial direction through hole, by above-mentioned annular groove, filler opening 21 is communicated with the first oil suction axis hole 30 and the second oil suction axis hole 36, and oil outlet 23 is communicated with the first force feed axis hole 31 and the second force feed axis hole 35.
Pentacle weel 15 footpaths upwards have five radial through holes 33 in uniform way, when eccentric shaft 7 rotates, radial through hole 33 is alternately communicated with the first oil suction groove 29 or the first pressure oil groove 32, radial through hole 33 is also communicated with plunger cavity by the through hole on the plunger 3 of opposite position, between radial through hole 33 and plunger 3, pressure ring 28 is installed, pressure ring 28 has elasticity, while having relative movement between plunger 3 and pentacle weel 15, still keep good sealing, in another group pentacle weel transmission system 19 being arranged in parallel, there is structure same as described above.
Between described plunger 3 and pentacle weel 15, between pentacle weel 15 and eccentric shaft 7, all taked sealing between eccentric shaft 7 and filler opening 21, oil outlet 23.
Described plunger group 4 and pentacle weel transmission system 19 also can adopt single-row structure.
The present invention has the following advantages:
1) compact structure, transmission is simple.The two colonnade plug groups 4 that have been arranged in parallel in this pump can ten plunger groups 4 be worked simultaneously, in each several part motion mutual noninterference, utilize to greatest extent the space in the pump housing 27.This pump is driven pentacle weel 15 and then is promoted plunger 3 by eccentric shaft 7 and moves, and transmission link is rolling friction, and frictional force is little, succinctly reliable.
2) output flow is large, and flowed fluctuation is little.This pump plunger chamber diameter is larger, and plunger group 4 has ten groups, and total output is the summation of all plunger group 4 output capabilities, and therefore discharge capacity is larger, and multi-cylinder co-operation, and the output peak-to-valley value of each cylinder makes up mutually, can reduce significantly total flowed fluctuation.
3) be convenient to maintenance.The plunger 3 of this pump and plunger case 2 thereof are all the parts that is independent of the pump housing 27, by screw, are arranged on the pump housing 27, and processing is simple, cost is low, and have advantages of and can install fast, dismantle, and are convenient to assembling and maintenance.
4) volumetric efficiency is high.This pump adopts axle flow mode, and between plunger 3 and pentacle weel 15, between pentacle weel 15 and eccentric shaft 7, all taked seal approach between eccentric shaft 7 and filler opening 21, oil outlet 23, sealing is good, and volumetric efficiency is high, and capacity utilization ratio is high.
Accompanying drawing explanation
Fig. 1 is axial sectional view of the present invention.
Fig. 2 is the sectional view in the A-A cross section of Fig. 1 of the present invention.
Fig. 3 is the sectional view in the B-B cross section of Fig. 1 of the present invention.
Fig. 4 is the sectional view in the C-C cross section of Fig. 1 of the present invention.
Fig. 5 is the sectional view in the D-D cross section of Fig. 1 of the present invention.
Fig. 6 is that in Fig. 2 of the present invention, eccentric shaft turns over the view after 90 °.
Embodiment
Below in conjunction with accompanying drawing, the present invention is described in detail.
See figures.1.and.2, a kind of axial-flow type biserial radial plunger oil hydraulic pump, comprise the pump housing 27, ten groups of plunger groups 4 are installed altogether on the pump housing 27, ten groups of plunger groups 4 are double-row parallel and arrange, the plunger group 4 of every row is radial and is evenly arranged, every group of plunger group 4 comprises plunger case gland 1, plunger case 2 and plunger 3, plunger case gland 1 is arranged on plunger case 2 bottoms, plunger 3 inserts from the other end of plunger case 2, at the interior straight line motion of plunger case 2, the tapped hole that screw screws on the pump housing 27 through the flange on plunger case gland 1 and plunger case 2 achieves a fixed connection,
Pentacle weel transmission system 19 is also dually arrayed and is arranged on the eccentric part of eccentric shaft 7, and be connected with the plunger group 4 of corresponding position respectively, pentacle weel transmission system 19 comprises pentacle weel 15, the first rolling bearing 13, the second rolling bearing 17, the first pentacle weel end cap 12, the second pentacle weel end cap 18 and the first check ring 14, the second check ring 16 and needle roller 24, eccentric shaft 7 is arranged in the pump housing 27, pentacle weel 15 is arranged on the eccentric part of eccentric shaft 7, by the first rolling bearing 13 and the second rolling bearing 17, support, the first pentacle weel end cap 12 and the second pentacle weel end cap 18 are arranged on respectively pentacle weel 15 both sides, and with bolt, pass pentacle weel 15 and lock, the seam of the first pentacle weel end cap 12 and the second pentacle weel end cap 18 inside is pressed on the bearing outer ring of the first rolling bearing 13 and the second rolling bearing 17, the bearing inner race of the first rolling bearing 13 and the second rolling bearing 17 is pressed in respectively on the first check ring 14 and the second check ring 16 of installing on eccentric shaft 7, on every limit of pentacle weel 15, all have plural axial arc groove, needle roller 24 is installed in each arc groove, needle roller 24 can be in arc groove Free-rolling, on the first pentacle weel end cap 12 and the second pentacle weel end cap 18, there is flange 25, flange 25 is enclosed in all needle rollers 24 in arc groove separately, the backhaul flanging 26 of the first pentacle weel end cap 12 and the second pentacle weel end cap 18 outer rims fastens the square flange of plunger 3 bottoms, plunger 3 is against on needle roller 24, realize being connected of needle roller 24 and plunger 3, pentacle weel Mei Bian center is also separately installed with a pressure ring 28, pressure ring 28 props up plunger 3 bottoms, the oilhole at the center of plunger 3, radial oilhole 33 on oilhole and the pentacle weel 15 at pressure ring 28 centers keeps being communicated with when work,
The first abutment sleeve 11 is all installed on the shaft part at eccentric shaft 7 two ends successively, the 3rd rolling bearing 10, the second abutment sleeve 9 and the 4th rolling bearing 8, eccentric shaft 7 is bearing on the first pump end cap 5 and the second pump end cap 20 by the 3rd rolling bearing 10 and the 4th rolling bearing 8, the first pump end cap 5 and the second pump end cap 20 are arranged on respectively the both sides of the pump housing 27, the first axle head gland 6 is arranged on the first pump end cap 5, seam on the first axle head gland 6 is pushed down the outer ring of the 4th rolling bearing 8 of this side, the outer ring of the 4th rolling bearing 8 of opposite side is compressed by the shoulder of the second pump end cap 20 inside, the second axle head gland 22 is arranged on the second pump end cap 20, axial aperture on eccentric shaft 7 is sealed.
With reference to Fig. 1, Fig. 2 and Fig. 3, in the eccentric part of eccentric shaft 7, all have symmetrically two arc grooves, wherein the first oil suction groove 29 and the first pressure oil groove 32 are one group and are positioned in same eccentric part, the second oil suction groove 37 and the second pressure oil groove 34 are one group and are positioned in another eccentric part, every group of arc groove is all about the axial plane of symmetry symmetry of eccentric shaft 7, and differ 180 ° between two groups of arc grooves, on eccentric shaft, also have the first oil suction axis hole 30, the first force feed axis hole 31, the second oil suction axis hole 36 and the second force feed axis hole 35, these four axis holes are uniform centered by the center of rotation of eccentric shaft 7, its distribution radius is about the half of least radius on eccentric shaft 7, and the first oil suction axis hole 30 and the second oil suction axis hole 36 differ 180 °, the first force feed axis hole 31 and the second force feed axis hole 35 differ 180 °, the first oil suction axis hole 30 and the first force feed axis hole 31 are communicated with by radial hole with the first oil suction groove 29 and the first pressure oil groove 32 respectively, the second oil suction axis hole 36 and the second force feed axis hole 35 are communicated with the second oil suction groove 37 and the second pressure oil groove 34 respectively, with reference to Fig. 1, Fig. 4, Fig. 5, one end that eccentric shaft 7 coordinates with the second pump end cap 20, be provided with two annular grooves its partial parallel near axle head, between two annular grooves and on the shaft part of both sides, seal ring is all installed, one of them annular groove is communicated with the first oil suction axis hole 30 and the second oil suction axis hole 36 by radial direction through hole, another annular groove is communicated with the first force feed axis hole 31 and the second force feed axis hole 35 by radial direction through hole, by above-mentioned annular groove, filler opening 21 is communicated with the first oil suction axis hole 30 and the second oil suction axis hole 36, oil outlet 23 is communicated with the first force feed axis hole 31 and the second force feed axis hole 35.
With reference to Fig. 1, pentacle weel 15 footpaths upwards have five radial through holes 33 in uniform way, when eccentric shaft 7 rotates, radial through hole 33 is alternately communicated with the first oil suction groove 29 or the first pressure oil groove 32, radial through hole 33 is also communicated with plunger cavity by the through hole on the plunger 3 of opposite position, between radial through hole 33 and plunger 3, pressure ring 28 is installed, and pressure ring 28 has elasticity, while having relative movement between plunger 3 and pentacle weel 15, still keep good sealing.In another group pentacle weel transmission system 19 being arranged in parallel, there is structure same as described above.
Between described plunger 3 and pentacle weel 15, between pentacle weel 15 and eccentric shaft 7, all taked sealing between eccentric shaft 7 and filler opening 21, oil outlet 23.
Described plunger group 4 and pentacle weel transmission system 19 also can adopt single-row structure.
Working principle of the present invention is:
Prime mover drives eccentric shaft 7 to rotate, eccentric part is by the first rolling bearing 13, the second rolling bearing 17 by transmission of power to pentacle weel 15, make pentacle weel 15 around rotating center rotating, owing to not rotating with the plunger 3 of pentacle weel connection, and each limit of plunger 3 bottom surfaces and pentacle weel 15 is adjacent to, therefore there is not rotation in pentacle weel 15, the motion of pentacle weel 15 drives plunger 3 to do straight reciprocating motion in chamber separately, there is relative sliding with the interplanar that pentacle weel 15 contacts in plunger 3, the rolling of passing through installed needle roller 24 reduces surface friction drag, when pentacle weel 15 promotes plunger 3 and is pressed into plunger cavity, thrust is transmitted by needle roller 24, when pentacle weel 15 drives plunger 3 backhaul, backhaul power is bestowed by the backhaul flanging 26 on the first pentacle weel end cap 12 and the second pentacle weel end cap 18 installed on pentacle weel 15.
With reference to Fig. 2, when eccentric shaft 7 is pressed the rotation of direction shown in figure, in this moment, in figure, each plunger 3 in left side is pressed into plunger cavity, and plunger cavity volume reduces, and the fluid in each chamber enters the first force feed axis hole 31 through the first pressure oil groove 32, and then discharges from oil outlet 23.In figure, each plunger 3 on right side is pulled out from plunger cavity, and plunger cavity volume increases, and the first oil suction groove 29 is connected in each chamber, by the first oil suction axis hole 30, from filler opening 21, sucks fluid.After eccentric shaft 7 turns over several angle, the oil suction of plunger cavity or force feed state also change thereupon, and mate with the rotation of eccentric shaft 7, Figure 6 shows that eccentric shaft 7 is with respect to the state in Fig. 1, the state of each plunger 3 while turning over 90 °; In another group structure being arranged in parallel, its working principle is identical.Ten plungers 3 are worked simultaneously, and then just inhalant liquid force feed from fuel tank continuously discharges from oil outlet, supplies with hydraulic system.
Claims (5)
1. an axial-flow type biserial radial plunger oil hydraulic pump, comprise the pump housing (27), it is characterized in that: ten groups of plunger groups (4) are installed altogether on the pump housing (27), ten groups of plunger groups (4) are double-row parallel and arrange, the plunger group (4) of every row is radial and is evenly arranged, every group of plunger group (4) comprises plunger case gland (1), plunger case (2) and plunger (3), plunger case gland (1) is arranged on plunger case (2) bottom, plunger (3) inserts from the other end of plunger case (2), straight line motion in plunger case (2), the tapped hole that screw screws on the pump housing (27) through the flange on plunger case gland (1) and plunger case (2) achieves a fixed connection,
Pentacle weel transmission system (19) is also dually arrayed and is arranged on the eccentric part of eccentric shaft (7), and be connected with the plunger group (4) of corresponding position respectively, pentacle weel transmission system (19) comprises pentacle weel (15), the first rolling bearing (13), the second rolling bearing (17), the first pentacle weel end cap (12), the second pentacle weel end cap (18) and the first check ring (14), the second check ring (16) and needle roller (24), eccentric shaft (7) is arranged in the pump housing (27), pentacle weel (15) is arranged on the eccentric part of eccentric shaft (7), by the first rolling bearing (13) and the second rolling bearing (17), support, the first pentacle weel end cap (12) and the second pentacle weel end cap (18) are arranged on respectively pentacle weel (15) both sides, and with bolt, pass pentacle weel (15) and lock, the inner seam of the first pentacle weel end cap (12) and the second pentacle weel end cap (18) is pressed on the bearing outer ring of the first rolling bearing (13) and the second rolling bearing (17), the bearing inner race of the first rolling bearing (13) and the second rolling bearing (17) is pressed in respectively on upper the first check ring (14) and the second check ring (16) of installing of eccentric shaft (7), on every limit of pentacle weel (15), all have plural axial arc groove, needle roller (24) is installed in each arc groove, needle roller (24) can be in arc groove Free-rolling, on the first pentacle weel end cap (12) and the second pentacle weel end cap (18), there is flange (25), flange (25) is enclosed in all needle rollers (24) in arc groove separately, the backhaul flanging (26) of the first pentacle weel end cap (12) and the second pentacle weel end cap (18) outer rim fastens the square flange of plunger (3) bottom, plunger (3) is against on needle roller (24), realize being connected of needle roller (24) and plunger (3), pentacle weel Mei Bian center is also separately installed with a pressure ring (28), pressure ring (28) props up plunger (3) bottom, the oilhole at the center of plunger (3), radial oilhole (33) on oilhole and the pentacle weel (15) at pressure ring (28) center keeps being communicated with when work,
On the shaft part at eccentric shaft (7) two ends, the first abutment sleeve (11) is all installed successively, the 3rd rolling bearing (10), the second abutment sleeve (9) and the 4th rolling bearing (8), eccentric shaft (7) is bearing on the first pump end cap (5) and the second pump end cap (20) by the 3rd rolling bearing (10) and the 4th rolling bearing (8), the first pump end cap (5) and the second pump end cap (20) are arranged on respectively the both sides of the pump housing (27), the first axle head gland (6) is arranged on the first pump end cap (5), seam on the first axle head gland (6) is pushed down the outer ring of the 4th rolling bearing (8) of this side, the outer ring of the 4th rolling bearing (8) of opposite side is compressed by the inner shoulder of the second pump end cap (20), the second axle head gland (22) is arranged on the second pump end cap (20), axial aperture on eccentric shaft (7) is sealed.
2. a kind of axial-flow type biserial radial plunger oil hydraulic pump according to claim 1, it is characterized in that: in the eccentric part of eccentric shaft (7), all have symmetrically two arc grooves, wherein the first oil suction groove (29) and the first pressure oil groove (32) are one group and are positioned in same eccentric part, the second oil suction groove (37) and the second pressure oil groove (34) are one group and are positioned in another eccentric part, every group of arc groove is all about the axial plane of symmetry symmetry of eccentric shaft (7), and differ 180 ° between two groups of arc grooves, on eccentric shaft, also have the first oil suction axis hole (30), the first force feed axis hole (31), the second oil suction axis hole (36) and the second force feed axis hole (35), these four axis holes are uniform centered by the center of rotation of eccentric shaft (7), its distribution radius is the half of the upper least radius of eccentric shaft (7), and the first oil suction axis hole (30) differs 180 ° with the second oil suction axis hole (36), the first force feed axis hole (31) differs 180 ° with the second force feed axis hole (35), the first oil suction axis hole (30) and the first force feed axis hole (31) are communicated with by radial hole with the first oil suction groove (29) and the first pressure oil groove (32) respectively, the second oil suction axis hole (36) and the second force feed axis hole (35) are communicated with the second oil suction groove (37) and the second pressure oil groove (34) respectively, one end that eccentric shaft (7) coordinates with the second pump end cap (20), be provided with two annular grooves its partial parallel near axle head, between two annular grooves and on the shaft part of both sides, seal ring is all installed, one of them annular groove is communicated with the first oil suction axis hole (30) and the second oil suction axis hole (36) by radial direction through hole, another annular groove is communicated with the first force feed axis hole (31) and the second force feed axis hole (35) by radial direction through hole, by above-mentioned annular groove, filler opening (21) is communicated with the first oil suction axis hole (30) and the second oil suction axis hole (36), oil outlet (23) is communicated with the first force feed axis hole (31) and the second force feed axis hole (35).
3. a kind of axial-flow type biserial radial plunger oil hydraulic pump according to claim 1, it is characterized in that: pentacle weel (15) footpath upwards has five radial through holes (33) in uniform way, when eccentric shaft (7) rotates, radial through hole (33) is alternately communicated with the first oil suction groove (29) or the first pressure oil groove (32), radial through hole (33) is also communicated with plunger cavity by the through hole on the plunger (3) of opposite position, between radial through hole (33) and plunger (3), pressure ring (28) is installed, pressure ring (28) has elasticity, while having relative movement between plunger (3) and pentacle weel (15), still keep good sealing, in another group pentacle weel transmission system (19) being arranged in parallel, there is structure same as described above.
4. a kind of axial-flow type biserial radial plunger oil hydraulic pump according to claim 1, is characterized in that: between described plunger (3) and pentacle weel (15), between pentacle weel (15) and eccentric shaft (7), eccentric shaft (7) and filler opening (21), oil outlet all taked sealing between (23).
5. a kind of axial-flow type biserial radial plunger oil hydraulic pump according to claim 1, is characterized in that: described plunger group (4) and pentacle weel transmission system (19) also can adopt single-row structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310491946.8A CN103758721B (en) | 2013-10-18 | 2013-10-18 | A kind of axial-flow type biserial radial plunger hydraulic pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310491946.8A CN103758721B (en) | 2013-10-18 | 2013-10-18 | A kind of axial-flow type biserial radial plunger hydraulic pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103758721A true CN103758721A (en) | 2014-04-30 |
| CN103758721B CN103758721B (en) | 2016-02-24 |
Family
ID=50526015
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310491946.8A Active CN103758721B (en) | 2013-10-18 | 2013-10-18 | A kind of axial-flow type biserial radial plunger hydraulic pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103758721B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104832393A (en) * | 2015-04-16 | 2015-08-12 | 天津工程机械研究院 | Multiplex radial plunger pump |
| CN106014901A (en) * | 2016-06-21 | 2016-10-12 | 西安交通大学 | Pressure compensation type end face oil distribution double-row radial plunger variable pump with annular piston |
| CN106194637A (en) * | 2016-07-27 | 2016-12-07 | 西安交通大学 | A kind of servomotor directly drives the floating-cup type radial plunger pump of variable |
| CN106224191A (en) * | 2016-07-27 | 2016-12-14 | 西安交通大学 | A kind of radial piston variable displacement pump of floating-cup type piston shoes structure |
| CN106246488A (en) * | 2016-07-27 | 2016-12-21 | 西安交通大学 | A kind of floating-cup type radial plunger pump of the driven by servomotor variable of biserial plunger |
| CN108302033A (en) * | 2018-03-04 | 2018-07-20 | 太原理工大学 | The axial scalable cylinder component of a kind of high water base pluger type hydraulic pump or motor |
| CN109944759A (en) * | 2019-02-25 | 2019-06-28 | 浙江工业大学 | A kind of multiple rows of high-pressure radial multi-plunger variable pump of integral type |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106826148B (en) * | 2017-01-10 | 2019-01-08 | 西安交通大学 | The load of five-pointed star plunger and the low-cycle fatigue cracking apparatus of Split link cracking |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5823091A (en) * | 1996-05-23 | 1998-10-20 | Lucas Industries, Plc | Radial piston pump having means for selectively disabling at least one of the pumping chambers |
| DE10300144B3 (en) * | 2003-01-07 | 2004-05-19 | Siemens Ag | Radial piston pump comprises a sliding block and a support piston connected by a form-locking snap-in connection |
| CN201354718Y (en) * | 2009-02-25 | 2009-12-02 | 杭州萧山东方液压件有限公司 | Multi-cylinder radial plunger pump |
| CN102155367A (en) * | 2011-03-11 | 2011-08-17 | 西安交通大学 | Fully-balanced type double-row radial plunger pump |
| CN203161433U (en) * | 2013-03-12 | 2013-08-28 | 佛山市顺德区中意液压有限公司 | Wear-resistant and stable bidirectional radial plunger type hydraulic motor eccentric structure |
-
2013
- 2013-10-18 CN CN201310491946.8A patent/CN103758721B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5823091A (en) * | 1996-05-23 | 1998-10-20 | Lucas Industries, Plc | Radial piston pump having means for selectively disabling at least one of the pumping chambers |
| DE10300144B3 (en) * | 2003-01-07 | 2004-05-19 | Siemens Ag | Radial piston pump comprises a sliding block and a support piston connected by a form-locking snap-in connection |
| CN201354718Y (en) * | 2009-02-25 | 2009-12-02 | 杭州萧山东方液压件有限公司 | Multi-cylinder radial plunger pump |
| CN102155367A (en) * | 2011-03-11 | 2011-08-17 | 西安交通大学 | Fully-balanced type double-row radial plunger pump |
| CN203161433U (en) * | 2013-03-12 | 2013-08-28 | 佛山市顺德区中意液压有限公司 | Wear-resistant and stable bidirectional radial plunger type hydraulic motor eccentric structure |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104832393A (en) * | 2015-04-16 | 2015-08-12 | 天津工程机械研究院 | Multiplex radial plunger pump |
| CN106014901A (en) * | 2016-06-21 | 2016-10-12 | 西安交通大学 | Pressure compensation type end face oil distribution double-row radial plunger variable pump with annular piston |
| CN106014901B (en) * | 2016-06-21 | 2018-01-16 | 西安交通大学 | A kind of pressure-compensated end face oil distributing biserial radial piston variable displacement pump of annular piston |
| CN106194637A (en) * | 2016-07-27 | 2016-12-07 | 西安交通大学 | A kind of servomotor directly drives the floating-cup type radial plunger pump of variable |
| CN106224191A (en) * | 2016-07-27 | 2016-12-14 | 西安交通大学 | A kind of radial piston variable displacement pump of floating-cup type piston shoes structure |
| CN106246488A (en) * | 2016-07-27 | 2016-12-21 | 西安交通大学 | A kind of floating-cup type radial plunger pump of the driven by servomotor variable of biserial plunger |
| CN106224191B (en) * | 2016-07-27 | 2018-04-17 | 西安交通大学 | A kind of radial piston variable displacement pump of floating-cup type piston shoes structure |
| CN106246488B (en) * | 2016-07-27 | 2018-04-17 | 西安交通大学 | A kind of floating-cup type radial plunger pump of the servomotor driving variable of biserial plunger |
| CN108302033A (en) * | 2018-03-04 | 2018-07-20 | 太原理工大学 | The axial scalable cylinder component of a kind of high water base pluger type hydraulic pump or motor |
| CN108302033B (en) * | 2018-03-04 | 2024-05-14 | 太原理工大学 | Axial telescopic cylinder assembly of high water-based plunger type hydraulic pump |
| CN109944759A (en) * | 2019-02-25 | 2019-06-28 | 浙江工业大学 | A kind of multiple rows of high-pressure radial multi-plunger variable pump of integral type |
| CN109944759B (en) * | 2019-02-25 | 2024-05-03 | 浙江工业大学 | Integrated multi-row high-pressure radial multi-plunger variable pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103758721B (en) | 2016-02-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103758721B (en) | A kind of axial-flow type biserial radial plunger hydraulic pump | |
| CN103742378B (en) | A kind of radial plunger hydraulic pump adopting guiding valve flow | |
| CN104358664B (en) | A kind of end face oil distributing without axial force biserial radial plunger pump | |
| CN103696921B (en) | A kind of valve flow distribution radial plunger oil hydraulic pump adopting hydraulic coupling backhaul | |
| CN103967731B (en) | A kind of end cam drive-type axial piston pump adopting flow ring to join oil | |
| CN108301999B (en) | A kind of two-dimentional plunger pump of space cam transmission | |
| CN113309681B (en) | Star-shaped high-pressure radial plunger pump | |
| CN102734108A (en) | Four-cylinder slurry pump | |
| CN104196693B (en) | Reciprocating four cylinder slush pumps | |
| CN103256217A (en) | Axial plunger pump return-stroke mechanism | |
| CN103758720B (en) | The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing | |
| CN104389754B (en) | A kind of compensation hydraulic formula radial plunger pump of end face oil distributing | |
| CN108302021B (en) | Submersible well type single-cylinder vertical plunger oil pump | |
| CN210889238U (en) | High-pressure pump | |
| CN101886631B (en) | Parallel move rotor type capacity-varied device | |
| CN212898899U (en) | Submersible single-cylinder plunger oil pump | |
| CN210396989U (en) | Quantitative radial oil distribution pump | |
| CN208456793U (en) | Reciprocating intensifier pump | |
| CN210290028U (en) | Variable radial oil distribution pump | |
| CN216518442U (en) | Pump head of plunger pump | |
| CN111622943B (en) | Submersible well type single-cylinder plunger oil pump | |
| CN220452138U (en) | Double-acting circulating pump | |
| US10876522B2 (en) | Insert type rotor for radial piston device | |
| CN220452140U (en) | Single-action circulating pump | |
| CN220828312U (en) | Integrated circulation liquid seal compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Application publication date: 20140430 Assignee: JIANGSU DALONGKAI TECHNOLOGY Co.,Ltd. Assignor: XI'AN JIAOTONG University Contract record no.: X2023980034024 Denomination of invention: A dual row radial piston hydraulic pump with axial flow distribution Granted publication date: 20160224 License type: Common License Record date: 20230324 |