CN103758720B - The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing - Google Patents
The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing Download PDFInfo
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- CN103758720B CN103758720B CN201310491895.9A CN201310491895A CN103758720B CN 103758720 B CN103758720 B CN 103758720B CN 201310491895 A CN201310491895 A CN 201310491895A CN 103758720 B CN103758720 B CN 103758720B
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Abstract
The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in employing, and be arranged in parallel in this pump two colonnade plug groups, takes full advantage of the space in pump, this pump carries out conversion of motion by pentacle weel transmission system, transmission link is rolling friction, and frictional force is little, succinctly reliably; This pump output capability is the comprehensive of all plunger cases output, and therefore discharge capacity is comparatively large, and during multi-cylinder co-operation, the output peak-to-valley value of each cylinder makes up mutually, can reduce total flowed fluctuation significantly; The plunger group of this pump is arranged on the pump housing by screw from outside, can realize dismantling fast, be easy for installation and maintenance, guide ring, the seal ring combination seal of active part many employings standard in the oil circuit of this pump, and sealing is reliable, is beneficial to the volumetric efficiency improving pump.
Description
Technical field
The invention belongs to radial plunger hydraulic pump technical field, be specifically related to a kind of employing join oil-piping layout join oil axial-flow type radial plunger hydraulic pump.
Background technique
Oil hydraulic pump effect is for hydraulic system provides the pressure oil with certain bearing capacity, the leakage of hydraulic oil in friction between the inner drive mechanism of oil hydraulic pump and runner, the main cause of produce power loss when being hydraulic pump works, therefore develop a kind of internal friction resistance little, the oil hydraulic pump of good seal performance is the effective means improving system capacity utilization ratio.
Radial plunger pump is large with flow, the advantage little, volumetric efficiency is high of wearing and tearing is widely used in the hydraulic system of the operations involving high pressures such as die casting, injection moulding, forging and stamping.The radial plunger pump of transmission generally adopts connecting rod, mostly is single cylinder, twin-tub, triplex structure.Output flow is limited, and fluctuation is larger.Because transmission adopts connecting rod, the link that wherein rubs is more, and therefore drag losses is many, and is unfavorable for the working life of improving the component such as eccentric shaft.Traditional axle joins oily formula radial plunger hydraulic pump, because the fluid flow process between plunger cavity and pintle through the fitting surface of multiple relative movement, therefore in order to reduce the resistance between the friction pair of face, need will sacrifice certain sealability.
Summary of the invention
In order to overcome the shortcoming of above-mentioned prior art, the invention reside in and propose a kind of employing and join the axial-flow type radial plunger hydraulic pump that oil-piping layout joins oil, there is compact structure, transmission is simple, output flow is large, flowed fluctuation is little, be 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:.
The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing, comprise the pump housing 28, on the pump housing 28, ten groups of plunger groups 4 are installed altogether, be divided into two row to be arranged in parallel, five the plunger groups 4 often arranged are radially uniform, 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 other end of plunger case 2, straight line motion in plunger case 2, with screw through the flange on plunger case gland 1 and plunger case 2, and the tapped hole screwed on the pump housing 28, realize the connection of plunger group 4 on the pump housing 28,
Pentacle weel transmission system 19 is also in dually arrayed, be arranged in the eccentric part of the eccentric shaft 7 of the pump housing 28 inside, 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 25, pentacle weel 15 is arranged on 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 with bolt-through, 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 25 is installed in each arc groove, needle roller 25 can in arc groove Free-rolling, first pentacle weel end cap 12 and the second pentacle weel end cap 18 there is flange 26, all needle rollers 25 are enclosed in respective arc groove by flange 26, the backhaul flanging 27 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 25, realize the connection of plunger 3 and pentacle weel transmission system 19, the radial direction of pentacle weel 15 also has five radial through holes in uniform way, and through hole is slotted hole,
Join oil-piping layout system 20 also in dually arrayed, on thin shaft part in the middle part of the eccentric part being arranged on eccentric shaft 7, the outer cylinder of this shaft part is the cylndrical surface concentric with center of rotation, join oil-piping layout system 20 and comprise the first distribution oil ring sheet 35, two the second distribution oil ring sheets 34 and five join oil-piping layout 29, first distribution oil ring sheet 35 is connected with hinged bolts with two the second distribution oil ring sheets 34, form an annular element, its inside is a complete cylndrical surface, coordinate with the middle part shaft part of pintle eccentric part, each of joining oil-piping layout system 20 is joined oil-piping layout 29 one end and is inserted in the first distribution oil ring sheet 35, each that second distribution oil ring sheet 34 is offered is joined in oil-piping layout jack 36, the other end is each passed through the radial through hole 37 of pentacle weel on pentacle weel 15, the corresponding central through bore of plunger 3 and the through hole at plunger case gland 1 center, its exposed portion round nut is locked.
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 21 by the 3rd rolling bearing 10 and the 4th rolling bearing 8, first pump end cap 5 and the second pump end cap 21 are arranged on the both sides of the pump housing 28 respectively, be screwed, 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 21 inside, second axle head gland 23 is arranged on the second pump end cap 21, axial aperture on eccentric shaft 7 is sealed.
Thinner shaft part in the middle part of the eccentric part of eccentric shaft 7 has all symmetrically two arc grooves, wherein the first oil suction groove 30 and the first pressure oil groove 33 are one group, be positioned in same eccentric part, second oil suction groove 41 and the second pressure oil groove 38 are one group, be 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 7 also has the first oil suction axis hole 31, first force feed axis hole 32, second oil suction axis hole 40 and the second force feed axis hole 39, 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 31 differs 180 ° with the second oil suction axis hole 40, first force feed axis hole 32 differs 180 ° with the second force feed axis hole 39, first oil suction first oil suction axis hole 31 is communicated with by radial hole with the first pressure oil groove 33 with the first oil suction groove 30 respectively with the first force feed axis hole 32, second oil suction axis hole 40 is communicated with the second pressure oil groove 38 with the second oil suction groove 41 respectively with the second force feed axis hole 39, one end that eccentric shaft 7 coordinates with the second pump end cap 21, 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 40 with the first oil suction axis hole 31 by radial direction through hole, another annular groove is communicated with the second force feed axis hole 39 with the first force feed axis hole 32 by radial direction through hole, by above-mentioned annular groove, filler opening 22 is communicated with the second oil suction axis hole 40 with the first oil suction axis hole 31, and oil outlet 24 is communicated with the second force feed axis hole 39 with the first force feed axis hole 32.
Between plunger 3 and plunger case 2 inwall, between the center hole of joining oil-piping layout 29 and plunger 3 and join oil-piping layout 29 and join and all to pass through between oil-piping layout jack 36 guide ring is installed and square seal ring realizes leading and sealing.
Between plunger case gland 1 and plunger case 2, join between oil-piping layout 29 and plunger case gland 1 and sealed by O type circle.
Described plunger group 4, pentacle weel transmission system 19 and join oil-piping layout system 20 and 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, and totally ten groups of plunger groups 4, take full advantage of the space in pump.This pump carries out conversion of motion by pentacle weel transmission system 19, 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 3 chamber diameter is comparatively large, and number is many, and its output capability is the comprehensive of all plunger 3 cylinders output, and therefore discharge capacity is comparatively large, and during multi-cylinder co-operation, the output peak-to-valley value of each cylinder makes up mutually, can reduce total flowed fluctuation significantly.
3) easy to maintenance.The plunger group 4 of this pump is arranged on the pump housing 28 by screw from outside, can realize dismantling fast, be easy for installation and maintenance, and plunger group 4 is the parts independent of the pump housing 28, also has the advantage that processing is simple, cost is low.
4) sealing is reliable, volumetric efficiency is high.Guide ring, the seal ring combination seal of active part many employings standard in the oil circuit of this pump, sealing is reliable, is beneficial to the volumetric efficiency improving pump.
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 7 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, the axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing, comprise the pump housing 28, on the pump housing 28, ten groups of plunger groups 4 are installed altogether, be divided into two row to be arranged in parallel, five the plunger groups 4 often arranged are radially uniform, 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 other end of plunger case 2, can in plunger case 2 straight line motion, with screw through the flange on plunger case gland 1 and plunger case 2, and the tapped hole screwed on the pump housing 28, realize the connection of plunger group 4 on the pump housing 28.
See figures.1.and.2, pentacle weel transmission system 19 is also in dually arrayed, be arranged in the eccentric part of the eccentric shaft 7 of the pump housing 28 inside, 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 25, pentacle weel 15 is arranged on 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 with bolt-through, 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 25 is installed in each arc groove, needle roller 25 can in arc groove Free-rolling, first pentacle weel end cap 12 and the second pentacle weel end cap 18 there is flange 26, all needle rollers 25 are enclosed in respective arc groove by flange 26, the backhaul flanging 27 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 25, realize the connection of plunger 3 and pentacle weel transmission system 19, the radial direction of pentacle weel 15 also has five radial through holes in uniform way, and through hole is slotted hole.
See figures.1.and.2, join oil-piping layout system 20 also in dually arrayed, on thinner shaft part in the middle part of the eccentric part being arranged on eccentric shaft 7, the outer cylinder of this shaft part is the cylndrical surface concentric with center of rotation, join oil-piping layout system 20 and comprise the first distribution oil ring sheet 35, two the second distribution oil ring sheets 34 and five join oil-piping layout 29, first distribution oil ring sheet 35 is connected with hinged bolts with two the second distribution oil ring sheets 34, form an annular element, its inside is a complete cylndrical surface, coordinate with the middle part shaft part of pintle eccentric part, each of joining oil-piping layout system 20 is joined oil-piping layout 29 one end and is inserted in the first distribution oil ring sheet 35, each that second distribution oil ring sheet 34 is offered is joined in oil-piping layout jack 36, the shaftless axial location of this end, the other end is each passed through the radial through hole 37 of pentacle weel on pentacle weel 15, the corresponding central through bore of plunger 3 and the through hole at plunger case gland 1 center, its exposed portion round nut is locked.Joining oil-piping layout 29 inserts on one section of plunger 3 chamber, have plural hole, hole location is not outwards higher than plunger case gland 1, inwardly be not less than the element such as guide ring, seal ring installed in the center hole of plunger 3, by joining oil-piping layout system 20, the fluid in plunger 3 chamber can be guided on oil distributing shaft.
With reference to Fig. 1, Fig. 2 and Fig. 3, thinner shaft part in the middle part of the eccentric part of eccentric shaft 7 has all symmetrically two arc grooves, wherein the first oil suction groove 30 and the first pressure oil groove 33 are one group, be positioned in same eccentric part, second oil suction groove 41 and the second pressure oil groove 38 are one group, be 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, when eccentric shaft 7 rotates, arc groove joins the UNICOM that oil-piping layout 29 through hole replaces in oil-piping layout system 20 with joining, eccentric shaft 7 also has the first oil suction axis hole 31, first force feed axis hole 32, second oil suction axis hole 40 and the second force feed axis hole 39, 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 31 differs 180 ° with the second oil suction axis hole 40, first force feed axis hole 32 differs 180 ° with the second force feed axis hole 39, first oil suction axis hole 31 is communicated with by radial hole with the first pressure oil groove 33 with the first oil suction groove 30 respectively with the first force feed axis hole 32, second oil suction axis hole 40 is communicated with the second pressure oil groove 38 with the second oil suction groove 41 respectively with the second force feed axis hole 39, with reference to Fig. 1, Fig. 4 and Fig. 5, one end that eccentric shaft 7 coordinates with the second pump end cap 21, 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, isolate, one of them annular groove is communicated with the second oil suction axis hole 40 with the first oil suction axis hole 31 by radial direction through hole, another annular groove is communicated with the second force feed axis hole 39 with the first force feed axis hole 32 by radial direction through hole, by above-mentioned annular groove, filler opening 22 is communicated with the second oil suction axis hole 40 with the first oil suction axis hole 31, oil outlet 24 is communicated with the second force feed axis hole 39 with the first force feed axis hole 32.
With reference to Fig. 1, 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 21 by the 3rd rolling bearing 10 and the 4th rolling bearing 8, first pump end cap 5 and the second pump end cap 21 are arranged on the both sides of the pump housing 28 respectively, be screwed, 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 21 inside, second axle head gland 23 is arranged on the second pump end cap 21, axial aperture on eccentric shaft 7 is sealed.
Between plunger 3 and plunger case 2 inwall, between the center hole of joining oil-piping layout 29 and plunger 3 and join oil-piping layout 29 and join and all to pass through between oil-piping layout jack 36 guide ring is installed and square seal ring realizes leading and sealing.
Between plunger case gland 1 and plunger case 2, join between oil-piping layout 29 and plunger case gland 1 and sealed by O type circle.
Working principle of the present invention is:
With reference to Fig. 2, 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 15 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 25 reduces surface friction drag, pentacle weel 15 promotes plunger 3 when entering plunger cavity, thrust is transmitted by needle roller 25, when pentacle weel 15 drives plunger 3 backhaul, reverberation matrix method is bestowed by the backhaul flanging 27 on the first pentacle weel end cap 12 that pentacle weel 15 is installed and the second pentacle weel end cap 18, when pentacle weel 15 moves, join oil-piping layout system 20 do not move thereupon, the radial through hole on pentacle weel 15 is slotted hole, when can ensure relative movement occurs between which, can not mutually interfere.
With reference to Fig. 2, when eccentric shaft 7 presses the rotation of direction shown in figure, this moment, each plunger 3 being in left side in figure is pressed into plunger cavity, plunger cavity volume reduces, and the fluid in each chamber enters join oil-piping layout 29 by joining the hole that oil-piping layout 29 is offered, and flows out from the other end, now join oil-piping layout 29 to be just communicated with the first pressure oil groove 33, therefore fluid is by discharging from oil outlet 24 after the first force feed axis hole 32; Each plunger 3 being in right side in figure is pulled out by from plunger cavity, plunger cavity volume increases, now the oil-piping layout 29 of joining of corresponding position is communicated with the first oil suction groove 30, therefore after fluid flows into the axial oilhole eccentric shaft 7 from filler opening 22, enter through the first oil suction groove 30 and join oil-piping layout 29, and enter plunger cavity from the hole of joining oil-piping layout 29 and realize oil suction; 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, Fig. 6 be eccentric shaft 7 relative to the state in Fig. 1, turn over the state of each plunger 3 after 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 mailbox, then discharge from oil outlet 24, supply hydraulic system.
Described plunger group 4, pentacle weel transmission system 19 and join oil-piping layout system 20 and also can adopt single-row structure.
Claims (5)
1. an employing is joined oil-piping layout and is joined oily axial-flow type radial plunger hydraulic pump, comprise the pump housing (28), it is characterized in that: ten groups of plunger groups (4) are installed altogether on the pump housing (28), be divided into two row to be arranged in parallel, five the plunger groups (4) often arranged are radially uniform, 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), with screw through the flange on plunger case gland (1) and plunger case (2), and the tapped hole screwed on the pump housing (28), realize the connection of plunger group (4) on the pump housing (28),
Pentacle weel transmission system (19) is also in dually arrayed, be arranged in the eccentric part of the inner eccentric shaft (7) of the pump housing (28), 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 (25), pentacle weel (15) is arranged on eccentric shaft (7), by the first rolling bearing (13) and the second rolling bearing (17) supporting, 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 with bolt-through, 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) respectively, 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 (25) is installed in each arc groove, needle roller (25) can in arc groove Free-rolling, first pentacle weel end cap (12) and the second pentacle weel end cap (18) there is flange (26), all needle rollers (25) are enclosed in respective arc groove by flange (26), the backhaul flanging (27) 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 (25), realize the connection of plunger (3) and pentacle weel transmission system (19), the radial direction of pentacle weel (15) also has five radial through holes in uniform way, and through hole is slotted hole,
Join oil-piping layout system (20) also in dually arrayed, on thin shaft part in the middle part of the eccentric part being arranged on eccentric shaft (7), the outer cylinder of this shaft part is the cylndrical surface concentric with center of rotation, join oil-piping layout system (20) and comprise the first distribution oil ring sheet (35), two the second distribution oil ring sheets (34) and five join oil-piping layout (29), first distribution oil ring sheet (35) is connected with hinged bolts with two the second distribution oil ring sheets (34), form an annular element, its inside is a complete cylndrical surface, coordinate with the middle part shaft part of pintle eccentric part, each of joining oil-piping layout system (20) is joined oil-piping layout (29) one end and is inserted in the first distribution oil ring sheet (35), each that second distribution oil ring sheet (34) is offered is joined in oil-piping layout jack (36), the other end is each passed through the radial through hole of pentacle weel (37) on pentacle weel (15), the corresponding central through bore of plunger (3) and the through hole at plunger case gland (1) center, its exposed portion round nut is locked.
2. the axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing according to claim 1, it is characterized in that: 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 (21) by the 3rd rolling bearing (10) and the 4th rolling bearing (8), first pump end cap (5) and the second pump end cap (21) are arranged on the both sides of the pump housing (28) respectively, be screwed, 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 (21) is inner, second axle head gland (23) is arranged on the second pump end cap (21), axial aperture on eccentric shaft (7) is sealed.
3. the axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing according to claim 1, it is characterized in that: the thin shaft part in the middle part of the eccentric part of eccentric shaft (7) has all symmetrically two arc grooves, wherein the first oil suction groove (30) and the first pressure oil groove (33) are one group, be positioned in same eccentric part, second oil suction groove (41) and the second pressure oil groove (38) are one group, be 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 (7) also has the first oil suction axis hole (31), first force feed axis hole (32), second oil suction axis hole (40) and the second force feed axis hole (39), 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 (31) differs 180 ° with the second oil suction axis hole (40), first force feed axis hole (32) differs 180 ° with the second force feed axis hole (39), first oil suction axis hole (31) is communicated with by radial hole with the first pressure oil groove (33) with the first oil suction groove (30) respectively with the first force feed axis hole (32), second oil suction axis hole (40) is communicated with the second pressure oil groove (38) with the second oil suction groove (41) respectively with the second force feed axis hole (39), one end that eccentric shaft (7) coordinates with the second pump end cap (21), 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 (40) with the first oil suction axis hole (31) by radial direction through hole, another annular groove is communicated with the second force feed axis hole (39) with the first force feed axis hole (32) by radial direction through hole, by above-mentioned annular groove, filler opening (22) is communicated with the second oil suction axis hole (40) with the first oil suction axis hole (31), oil outlet (24) is communicated with the second force feed axis hole (39) with the first force feed axis hole (32).
4. the axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing according to claim 1, it is characterized in that: between plunger (3) and plunger case (2) inwall, between the center hole of joining oil-piping layout (29) and plunger (3) and join oil-piping layout (29) and join and all to pass through between oil-piping layout jack (36) to install guide ring and square seal ring realizes leading and sealing.
5. a kind of employing according to claim 1 join oil-piping layout join oil axial-flow type radial plunger hydraulic pump, it is characterized in that: between plunger case gland (1) and plunger case (2), join between oil-piping layout (29) and plunger case gland (1) pass through O type circle seal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310491895.9A CN103758720B (en) | 2013-10-18 | 2013-10-18 | The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310491895.9A CN103758720B (en) | 2013-10-18 | 2013-10-18 | The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing |
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| Publication Number | Publication Date |
|---|---|
| CN103758720A CN103758720A (en) | 2014-04-30 |
| CN103758720B true CN103758720B (en) | 2015-11-25 |
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| CN201310491895.9A Expired - Fee Related CN103758720B (en) | 2013-10-18 | 2013-10-18 | The axial-flow type radial plunger hydraulic pump that oil joined by oil-piping layout is joined in a kind of employing |
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| CN103982390B (en) * | 2014-05-20 | 2016-05-04 | 西安交通大学 | The end surface cam type single cylinder micrometeor plunger displacement pump that a kind of servomotor directly drives |
| CN114198277B (en) * | 2021-12-14 | 2023-03-31 | 浙江工业大学 | Gear drive reciprocating piston pump |
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| CN1699749A (en) * | 2004-05-18 | 2005-11-23 | 卢堃 | Swing angle type radial plunger variable pump |
| DE102009021832A1 (en) * | 2009-05-19 | 2010-11-25 | Robert Bosch Gmbh | Hydraulic pump is provided with displacement chambers having displacement units, where displacement chambers are provided with check valve with pressure line |
| CN101985921A (en) * | 2010-09-20 | 2011-03-16 | 余文凌 | External radial plunger pump of sealing mechanism |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2296087A1 (en) * | 1974-12-23 | 1976-07-23 | Poclain Sa | Hydraulic motor or pump with radial pistons - has offset spherical cam to reduce wear on piston shoes |
-
2013
- 2013-10-18 CN CN201310491895.9A patent/CN103758720B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB763095A (en) * | 1954-02-20 | 1956-12-05 | Donkin And Company Ltd | Improvements in and relating to hydraulic pumps and motors |
| US4242062A (en) * | 1979-08-06 | 1980-12-30 | Lear Siegler, Inc. | Dual piston pump with pressure seal lubrication feature |
| CN1699749A (en) * | 2004-05-18 | 2005-11-23 | 卢堃 | Swing angle type radial plunger variable pump |
| DE102009021832A1 (en) * | 2009-05-19 | 2010-11-25 | Robert Bosch Gmbh | Hydraulic pump is provided with displacement chambers having displacement units, where displacement chambers are provided with check valve with pressure line |
| CN101985921A (en) * | 2010-09-20 | 2011-03-16 | 余文凌 | External radial plunger pump of sealing mechanism |
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| Publication number | Publication date |
|---|---|
| CN103758720A (en) | 2014-04-30 |
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