CN103758721B - A kind of axial-flow type biserial radial plunger hydraulic pump - Google Patents

A kind of axial-flow type biserial radial plunger hydraulic pump Download PDF

Info

Publication number
CN103758721B
CN103758721B CN201310491946.8A CN201310491946A CN103758721B CN 103758721 B CN103758721 B CN 103758721B CN 201310491946 A CN201310491946 A CN 201310491946A CN 103758721 B CN103758721 B CN 103758721B
Authority
CN
China
Prior art keywords
plunger
pentacle weel
pump
axis hole
cap
Prior art date
Application number
CN201310491946.8A
Other languages
Chinese (zh)
Other versions
CN103758721A (en
Inventor
赵升吨
郭桐
张晨阳
刘辰
韩晓兰
Original Assignee
西安交通大学
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 西安交通大学 filed Critical 西安交通大学
Priority to CN201310491946.8A priority Critical patent/CN103758721B/en
Publication of CN103758721A publication Critical patent/CN103758721A/en
Application granted granted Critical
Publication of CN103758721B publication Critical patent/CN103758721B/en

Links

Abstract

A kind of axial-flow type biserial radial plunger hydraulic pump, be arranged in parallel in this pump two colonnade plug groups, while plunger group motion mutual noninterference, utilizes the space in the pump housing to greatest extent; This pump drives pentacle weel by eccentric shaft and then promotes plunger motion, transmission link is rolling friction, succinct reliable, the total output of this pump is the summation of all plunger group output capabilities, therefore discharge capacity is larger, and multi-cylinder co-operation, the output peak-to-valley value of each cylinder makes up mutually, total flowed fluctuation can be reduced significantly, the plunger of this pump and plunger case thereof are all the parts independent of the pump housing, processing is simple, cost is low, and has the advantage can installed fast, dismantle, and is convenient to assembling and maintenance; This pump adopts axle flow mode, and between plunger and pentacle weel, between pentacle weel and eccentric shaft, eccentric shaft and filler opening, all take seal approach between oil outlet, capacity utilization ratio is high.

Description

A kind of axial-flow type biserial radial plunger hydraulic pump
Technical field
The invention belongs to radial plunger hydraulic pump technical field, be specifically related to a kind of axial-flow type biserial radial plunger 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 producing leakage and noise simultaneously, in order to improve system capacity usage ratio, reduce vibration, one of the most effective way is exactly develop that volumetric efficiency is high, the oil hydraulic pump of flow trim.In all kinds of oil hydraulic pump, radial plunger hydraulic pump is widely used in the hydraulic system of all kinds of operations involving high pressure with its remarkable advantage that wearing and tearing are little, 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 carry out drive plunger move reciprocatingly in cylinder body, common are twin cylinder pump, triplex pump and five cylinder pumps etc. by eccentric shaft.This kind of pump is structurally difficult to the design realizing a fairly large number of plunger case, and thus the output flow fluctuation of pump is larger.In practice in order to reduce flowed fluctuation as far as possible, just need the length suitably increasing connecting rod, therefore, this type of pump has larger axial volume usually.In addition, be connected through the hinge between each component due to crank-link mechanism, transmission link is complicated, and there is dead center position, and 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 hydraulic pump, there is compact structure, transmission is simple, output flow is large, flowed fluctuation is little, being convenient to keep in repair and the high advantage of volumetric efficiency.
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 hydraulic pump, comprise the pump housing 27, the pump housing 27 is provided with ten groups of plunger groups 4 altogether, ten groups of plunger groups 4 are arranged in double-row parallel, the plunger group 4 often arranged radially is evenly arranged, often organize plunger group 4 and comprise plunger case gland 1, plunger case 2 and plunger 3, plunger case gland 1 is arranged on bottom plunger case 2, plunger 3 inserts from the top 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 arranged on the eccentric part of eccentric shaft 7 in dually arrayed, and be connected with the plunger group 4 of corresponding position respectively, pentacle weel transmission system 19 comprises pentacle weel 15, first rolling bearing 13, second rolling bearing 17, first pentacle weel end cap 12, second pentacle weel end cap 18 and the first check ring 14, 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, support by the first rolling bearing 13 and the second rolling bearing 17, first pentacle weel end cap 12 and the second pentacle weel end cap 18 are arranged on pentacle weel 15 both sides respectively, and lock through pentacle weel 15 with bolt, 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 on the first check ring 14 and the second check ring 16 that eccentric shaft 7 is installed respectively, every limit of pentacle weel 15 all has plural axial arc groove, needle roller 24 is installed in each arc groove, needle roller 24 can in arc groove Free-rolling, first pentacle weel end cap 12 and the second pentacle weel end cap 18 there is flange 25, all needle rollers 24 are enclosed in respective arc groove by flange 25, 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 bottom plunger 3, plunger 3 is against on needle roller 24, realize the connection of needle roller 24 and plunger 3, the center on the every limit of pentacle weel is also separately installed with a pressure ring 28, pressure ring 28 props up bottom plunger 3, the oilhole at the center of plunger 3, the oilhole at pressure ring 28 center operationally keeps being communicated with the radial oilhole 33 on pentacle weel 15,
The shaft part at eccentric shaft 7 two ends is provided with all successively the first abutment sleeve 11, 3rd rolling bearing 10, 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, first pump end cap 5 and the second pump end cap 20 are arranged on the both sides of the pump housing 27 respectively, first axle head gland 6 is arranged on the first pump end cap 5, seam on first axle head gland 6 pushes 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, second axle head gland 22 is arranged on the second pump end cap 20, axial aperture on eccentric shaft 7 is sealed.
The eccentric part of eccentric shaft 7 has all 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, second oil suction groove 37 and the second pressure oil groove 34 are one group and are positioned in another eccentric part, often organize the axial plane of symmetry of arc groove all about eccentric shaft 7 symmetrical, and differ 180 ° between two groups of arc grooves, eccentric shaft also has the first oil suction axis hole 30, first force feed axis hole 31, 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 differs 180 ° with the second oil suction axis hole 36, first force feed axis hole 31 differs 180 ° with the second force feed axis hole 35, first oil suction axis hole 30 is communicated with by radial hole with the first pressure oil groove 32 with the first oil suction groove 29 respectively with the first force feed axis hole 31, second oil suction axis hole 36 is communicated with the second pressure oil groove 34 with the second oil suction groove 37 respectively with the second force feed axis hole 35, one end that eccentric shaft 7 coordinates with the second pump end cap 20, its part near axle head is provided with two annular grooves abreast, all seal ring is installed between two annular grooves and on the shaft part of both sides, one of them annular groove is communicated with the second oil suction axis hole 36 with the first oil suction axis hole 30 by radial direction through hole, another annular groove is communicated with the second force feed axis hole 35 with the first force feed axis hole 31 by radial direction through hole, by above-mentioned annular groove, filler opening 21 is communicated with the second oil suction axis hole 36 with the first oil suction axis hole 30, and oil outlet 23 is communicated with the second force feed axis hole 35 with the first force feed axis hole 31.
Pentacle weel 15 radial direction has in uniform way five radial oilholes 33, when eccentric shaft 7 rotates, radial oilhole 33 is alternately communicated with the first oil suction groove 29 or the first pressure oil groove 32, radial oilhole 33 is also communicated with plunger cavity by the through hole on the plunger 3 of opposite position, between radial oilhole 33 and plunger 3, pressure ring 28 is installed, pressure ring 28 has elasticity, when having relative movement between plunger 3 and pentacle weel 15, still good sealing is kept, in another row pentacle weel transmission system 19 be 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, eccentric shaft 7 and filler opening 21, all take sealing between 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.Be arranged in parallel in this pump two colonnade plug groups 4, ten plunger groups 4 can work simultaneously, while each several part motion mutual noninterference, utilize the space in the pump housing 27 to greatest extent.This pump is driven pentacle weel 15 by eccentric shaft 7 and then is promoted plunger 3 and moves, and transmission link is rolling friction, and frictional force is little, succinctly reliably.
2) output flow is large, and flowed fluctuation is little.This pump plunger chamber diameter is comparatively large, 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 comparatively large, and multi-cylinder co-operation, the output peak-to-valley value of each cylinder makes up mutually, can reduce total flowed fluctuation significantly.
3) maintenance is convenient to.The plunger 3 of this pump and plunger case 2 thereof are all the parts independent of the pump housing 27, are arranged on the pump housing 27 by screw, and processing is simple, cost is low, and has the advantage can installed 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, eccentric shaft 7 and filler opening 21, all take seal approach between 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 hydraulic pump, comprise the pump housing 27, the pump housing 27 is provided with ten groups of plunger groups 4 altogether, ten groups of plunger groups 4 are arranged in double-row parallel, the plunger group 4 often arranged radially is evenly arranged, often organize plunger group 4 and comprise plunger case gland 1, plunger case 2 and plunger 3, plunger case gland 1 is arranged on bottom plunger case 2, plunger 3 inserts from the top 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 arranged on the eccentric part of eccentric shaft 7 in dually arrayed, and be connected with the plunger group 4 of corresponding position respectively, pentacle weel transmission system 19 comprises pentacle weel 15, first rolling bearing 13, second rolling bearing 17, first pentacle weel end cap 12, second pentacle weel end cap 18 and the first check ring 14, 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, support by the first rolling bearing 13 and the second rolling bearing 17, first pentacle weel end cap 12 and the second pentacle weel end cap 18 are arranged on pentacle weel 15 both sides respectively, and lock through pentacle weel 15 with bolt, 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 on the first check ring 14 and the second check ring 16 that eccentric shaft 7 is installed respectively, every limit of pentacle weel 15 all has plural axial arc groove, needle roller 24 is installed in each arc groove, needle roller 24 can in arc groove Free-rolling, first pentacle weel end cap 12 and the second pentacle weel end cap 18 there is flange 25, all needle rollers 24 are enclosed in respective arc groove by flange 25, 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 bottom plunger 3, plunger 3 is against on needle roller 24, realize the connection of needle roller 24 and plunger 3, the center on the every limit of pentacle weel is also separately installed with a pressure ring 28, pressure ring 28 props up bottom plunger 3, the oilhole at the center of plunger 3, the oilhole at pressure ring 28 center operationally keeps being communicated with the radial oilhole 33 on pentacle weel 15,
The shaft part at eccentric shaft 7 two ends is provided with all successively the first abutment sleeve 11, 3rd rolling bearing 10, 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, first pump end cap 5 and the second pump end cap 20 are arranged on the both sides of the pump housing 27 respectively, first axle head gland 6 is arranged on the first pump end cap 5, seam on first axle head gland 6 pushes 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, 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, the eccentric part of eccentric shaft 7 has all 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, second oil suction groove 37 and the second pressure oil groove 34 are one group and are positioned in another eccentric part, often organize the axial plane of symmetry of arc groove all about eccentric shaft 7 symmetrical, and differ 180 ° between two groups of arc grooves, eccentric shaft also has the first oil suction axis hole 30, first force feed axis hole 31, 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 differs 180 ° with the second oil suction axis hole 36, first force feed axis hole 31 differs 180 ° with the second force feed axis hole 35, first oil suction axis hole 30 is communicated with by radial hole with the first pressure oil groove 32 with the first oil suction groove 29 respectively with the first force feed axis hole 31, second oil suction axis hole 36 is communicated with the second pressure oil groove 34 with the second oil suction groove 37 respectively with the second force feed axis hole 35, with reference to Fig. 1, Fig. 4, Fig. 5, one end that eccentric shaft 7 coordinates with the second pump end cap 20, its part near axle head is provided with two annular grooves abreast, all seal ring is installed between two annular grooves and on the shaft part of both sides, one of them annular groove is communicated with the second oil suction axis hole 36 with the first oil suction axis hole 30 by radial direction through hole, another annular groove is communicated with the second force feed axis hole 35 with the first force feed axis hole 31 by radial direction through hole, by above-mentioned annular groove, filler opening 21 is communicated with the second oil suction axis hole 36 with the first oil suction axis hole 30, oil outlet 23 is communicated with the second force feed axis hole 35 with the first force feed axis hole 31.
With reference to Fig. 1, pentacle weel 15 radial direction has in uniform way five radial oilholes 33, when eccentric shaft 7 rotates, radial oilhole 33 is alternately communicated with the first oil suction groove 29 or the first pressure oil groove 32, radial oilhole 33 is also communicated with plunger cavity by the through hole on the plunger 3 of opposite position, and be provided with pressure ring 28 between radial oilhole 33 and plunger 3, pressure ring 28 has elasticity, when having relative movement between plunger 3 and pentacle weel 15, still keep good sealing.In another row pentacle weel transmission system 19 be 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, eccentric shaft 7 and filler opening 21, all take sealing between 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, second rolling bearing 17 by transmission of power to pentacle weel 15, make pentacle weel 15 around rotation center rotating, because the plunger 3 connect with pentacle weel does not rotate, and each limit of plunger 3 bottom surface 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 respective chamber, there is relative sliding in the interplanar that plunger 3 contacts with pentacle weel 15, the rolling passing through installed needle roller 24 reduces surface friction drag, pentacle weel 15 promotes plunger 3 when being pressed into plunger cavity, thrust is transmitted by needle roller 24, when pentacle weel 15 drives plunger 3 backhaul, reverberation matrix method is bestowed by the backhaul flanging 26 on the first pentacle weel end cap 12 that pentacle weel 15 is installed and the second pentacle weel end cap 18.
With reference to Fig. 2, when eccentric shaft 7 presses the rotation of direction shown in figure, in this moment, each plunger 3 being in left side in figure 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.Each plunger 3 being in right side in figure is pulled out by from plunger cavity, and plunger cavity volume increases, and the first oil suction groove 29 is connected in each chamber, sucks fluid by the first oil suction axis hole 30 from filler opening 21.After eccentric shaft 7 turns over several angle, oil suction or the force feed state of plunger cavity also change thereupon, and mate with the rotation of eccentric shaft 7, Figure 6 shows that eccentric shaft 7 is relative to the state in Fig. 1, the state of each plunger 3 when turning over 90 °; In another group structure be arranged in parallel, its working principle is identical.Ten plungers 3 work simultaneously, just can continuously inhalant liquid force feed from fuel tank, then discharge from oil outlet, supply hydraulic system.

Claims (4)

1. an axial-flow type biserial radial plunger 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 arranged in double-row parallel, the plunger group (4) often arranged radially is evenly arranged, often organize plunger group (4) and comprise 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 top 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) in dually arrayed is arranged on the eccentric part of eccentric shaft (7), and be connected with the plunger group (4) of corresponding position respectively, wherein a row pentacle weel transmission system (19) comprises pentacle weel (15), first rolling bearing (13), second rolling bearing (17), first pentacle weel end cap (12), second pentacle weel end cap (18) and the first check ring (14), 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), support by the first rolling bearing (13) and the second rolling bearing (17), first pentacle weel end cap (12) and the second pentacle weel end cap (18) are arranged on pentacle weel (15) both sides respectively, and with bolt through pentacle weel (15) locking, 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 on upper the first check ring (14) installed of eccentric shaft (7) and the second check ring (16) respectively, every limit of pentacle weel (15) all has plural axial arc groove, needle roller (24) is installed in each arc groove, needle roller (24) can in arc groove Free-rolling, first pentacle weel end cap (12) and the second pentacle weel end cap (18) there is flange (25), all needle rollers (24) are enclosed in respective arc groove by flange (25), 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 the connection of needle roller (24) and plunger (3), the center on the every limit of pentacle weel 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), the oilhole at pressure ring (28) center operationally keeps being communicated with the radial oilhole (33) on pentacle weel (15),
The shaft part at eccentric shaft (7) two ends is provided with all successively the first abutment sleeve (11), 3rd rolling bearing (10), 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), first pump end cap (5) and the second pump end cap (20) are arranged on the both sides of the pump housing (27) respectively, first axle head gland (6) is arranged on the first pump end cap (5), seam on first axle head gland (6) pushes 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 that the second pump end cap (20) is inner, 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 hydraulic pump according to claim 1, it is characterized in that: the eccentric part of eccentric shaft (7) has all 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, second oil suction groove (37) and the second pressure oil groove (34) are one group and are positioned in another eccentric part, often organize the axial plane of symmetry of arc groove all about eccentric shaft (7) symmetrical, and differ 180 ° between two groups of arc grooves, eccentric shaft also has the first oil suction axis hole (30), first force feed axis hole (31), 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), first force feed axis hole (31) differs 180 ° with the second force feed axis hole (35), first oil suction axis hole (30) is communicated with by radial hole with the first pressure oil groove (32) with the first oil suction groove (29) respectively with the first force feed axis hole (31), second oil suction axis hole (36) is communicated with the second pressure oil groove (34) with the second oil suction groove (37) respectively with the second force feed axis hole (35), one end that eccentric shaft (7) coordinates with the second pump end cap (20), its part near axle head is provided with two annular grooves abreast, all seal ring is installed between two annular grooves and on the shaft part of both sides, one of them annular groove is communicated with the second oil suction axis hole (36) with the first oil suction axis hole (30) by radial direction through hole, another annular groove is communicated with the second force feed axis hole (35) with the first force feed axis hole (31) by radial direction through hole, by above-mentioned annular groove, filler opening (21) is communicated with the second oil suction axis hole (36) with the first oil suction axis hole (30), oil outlet (23) is communicated with the second force feed axis hole (35) with the first force feed axis hole (31).
3. a kind of axial-flow type biserial radial plunger hydraulic pump according to claim 1, it is characterized in that: pentacle weel (15) radial direction has in uniform way five radial oilholes (33), when eccentric shaft (7) rotates, radial oilhole (33) is alternately communicated with the first oil suction groove (29) or the first pressure oil groove (32), radial oilhole (33) is also communicated with plunger cavity by the through hole on the plunger (3) of opposite position, pressure ring (28) is installed between radial oilhole (33) and plunger (3), pressure ring (28) has elasticity, when having relative movement between plunger (3) and pentacle weel (15), still good sealing is kept, another row pentacle weel transmission system (19) be arranged in parallel, have and the described structure that wherein a row pentacle weel transmission system (19) is identical.
4. a kind of axial-flow type biserial radial plunger 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 take sealing between (23).
CN201310491946.8A 2013-10-18 2013-10-18 A kind of axial-flow type biserial radial plunger hydraulic pump CN103758721B (en)

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 CN103758721A (en) 2014-04-30
CN103758721B true CN103758721B (en) 2016-02-24

Family

ID=50526015

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310491946.8A 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 (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106826148A (en) * 2017-01-10 2017-06-13 西安交通大学 The loading of five-pointed star plunger and the low-cycle fatigue cracking apparatus of Split link cracking

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104832393B (en) * 2015-04-16 2017-04-12 天津工程机械研究院 Multiplex radial plunger pump
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
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
CN106194637B (en) * 2016-07-27 2018-04-17 西安交通大学 A kind of servomotor directly drives the floating-cup type radial plunger pump of variable

Citations (5)

* Cited by examiner, † Cited by third party
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
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 (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106826148A (en) * 2017-01-10 2017-06-13 西安交通大学 The loading of five-pointed star plunger and the low-cycle fatigue cracking apparatus of Split link cracking
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

Also Published As

Publication number Publication date
CN103758721A (en) 2014-04-30

Similar Documents

Publication Publication Date Title
US8465268B2 (en) Compression clamp for a modular fluid end for a multiplex plunger pump
US3223046A (en) Rotary radial piston machines
AU2009232511B2 (en) Device with rotary pistons that can be used as a compressor, a pump, a vacuum pump, a turbine, a motor and as other driving and driven hydraulic-pneumatic machines
US20200166026A1 (en) Direct drive pump assemblies
CN201116524Y (en) Valve-type oil distribution and inclined disc drive axial direction reciprocating pump lubrication device
CN204493095U (en) Hydraulic bidirectional effect pumping installations
CN101985921B (en) External radial plunger pump of casing tongue sealing mechanism
US2130299A (en) Radial pump
CN209800178U (en) reciprocating type three-cylinder plunger pump for oil and gas field
CN105317670B (en) Magnetic suspension sloping tray axial plunger piston pump
CN204357643U (en) A kind of swash plate rotary internal Flat valve axial piston pump
CN104612928A (en) Hydraulic bidirectional pumping device
CN101131152A (en) Constant-pressure variable radial-plunger pump
CN104005924A (en) High-power radial plunger pump
CN103261661B (en) High-pressure service pump
CN111692065A (en) Plunger pump hydraulic end
US3413929A (en) Radial piston pump
WO2018014472A1 (en) Two-dimensional tapered roller piston pump
CN103233873B (en) External-rotor radial plunger hydraulic pump integrated with motors
CN104454420A (en) Inclined-disc-rotating internally-disposed valve flow distribution axial plunger pump
CN103939311B (en) A kind of hydraulic pressure backhaul radial plunger pump adopting biserial guiding valve to join oil
CN109882372A (en) A kind of reciprocating three-cylinder plunger pump of oil gas field
CN101876302B (en) Multi-cylinder reciprocating pump
CN2900863Y (en) Automatic compensating plunger seal device for well drilling pump
CN104329232B (en) The radial plunger pump of the integral type that a kind of permanent magnet disc motor drives

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