CN1074019A - The assignment method of low-noise axial plunger pump and port plate structure - Google Patents
The assignment method of low-noise axial plunger pump and port plate structure Download PDFInfo
- Publication number
- CN1074019A CN1074019A CN 91111998 CN91111998A CN1074019A CN 1074019 A CN1074019 A CN 1074019A CN 91111998 CN91111998 CN 91111998 CN 91111998 A CN91111998 A CN 91111998A CN 1074019 A CN1074019 A CN 1074019A
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- oil
- flow groove
- plunger
- groove
- oil extraction
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Abstract
The present invention is a kind of assignment method and port plate structure of axial piston pump, that thrust plate adopts is asymmetric, the circumferential cornerite of its oil extraction flow groove is less than the circumferential cornerite of oil suction flow groove, turn to identically at the deflection direction at the mispairing angle of press area and rotor, and it is in the deflection direction at the mispairing angle in release of pressure district and the switched in opposite of rotor.The working life that the present invention can reduce the noise of pump and improve the flow pair.
Description
The present invention is the assignment method of a kind of low-noise axial plunger pump in the hydraulic machinery and the port plate structure that adopts a kind of novel axial plunger pump of this method design.
Fig. 1 is a scheme of erection of the present invention, Fig. 2 is the structural representation of thrust plate of the present invention, Fig. 3 be the thrust plate among Fig. 2 I-I to sectional view, Fig. 4 is the geometrical construction figure of thrust plate of the present invention, plunger 7 is called dead point axle in projection on the thrust plate 4 and plunger 7 at the line of the dead point of oil suction stroke between the projection on the thrust plate 4 at the dead point of oil extraction stroke, be Fig. 2, Y-Y ' axle among Fig. 4, Fig. 2, plane 12, two intervals among Fig. 4,12 ' the bisector of cornerite be respectively ON, ON ', ON and ON ' are called the mispairing angle with the angle of Y-Y ' axle, vibration damping groove (hole) 14 among Fig. 4,14 ' be called the choke-out angle at the cornerite of garden Zhou Fangxiang.
The flow distributing noise of the thrust plate of axial piston pump is the main noise source of axial piston pump.Axial piston pump assignment method of the prior art is based on the thought that no flow impacts in the hyperbaric chamber, port plate structure adopts symmetric deflection formula structure, be the cornerite that the cornerite of oil suction flow groove equals oil extraction flow groove, turning to of two mispairing angles is all identical with turning to of rotor.
The noise that adopts above-mentioned assignment method of the prior art and port plate structure in actual motion, to keep away unavoidably in assignment process, to make fluid to produce air pocket and produced because of the air pocket vibration.When the oil cylinder disengaging oil extraction flow groove of plunger enters oil extraction flow groove to the plane, interval (release of pressure district) between the oil suction flow groove, the oil cylinder that is far smaller than plunger by the initial volume of the fluid of mechanical close in the oil cylinder breaks away from the initial volume of the fluid that oil suction flow groove is closed the oil cylinder when entering from the plane, interval (press area) of oil suction flow groove to oil extraction flow groove, oil cylinder enters press area in the scope at choke-out angle, oil pressure rises to oil extraction pressure from oil suction pressure, after oil cylinder enters the release of pressure district, certainly existed the release of pressure phenomenon, and because the rotor of axial piston pump is subjected to force unbalance, make and form uneven wedge-type seal gap between rotor end-face and the thrust plate working surface, the angle of wedge increases with the increase of the load of pump, make oil cylinder 5 oil pressure that enter sealing release of pressure district shift to an earlier date decompression because of this gap, the oil cylinder after the decompression proceeds to seal mechanical swelling again can cause serious release of pressure phenomenon excessively.Young's modulus because of fluid is very big again, crosses release of pressure and makes the very big degree of vacuum of generation in the oil cylinder, and this instantaneous vacuum makes fluid produce air pocket, and when the fluid that contains air pocket was brought to oil extraction flow groove, the broken air pocket that forms of air pocket vibrated, and produces strong noise.
The present invention is a kind of assignment method and port plate structure of low-noise axial plunger pump, periodically slip over two flow grooves 11 on the thrust plate 4 at the oil cylinder 5 of the plunger on the rotor 67,15, (turn to identical) respectively at oil suction flow groove 11 in the counterclockwise direction with rotor 6, the end of oil extraction flow groove 15 has a vibration damping groove (hole) 14,14 ', assignment method of the present invention is characterised in that, the geometric distribution of two flow grooves adopts non-symmetry structure, be the cornerite of the cornerite of oil extraction flow groove less than oil suction flow groove, the oil extraction stroke of plunger is not finished, the oil cylinder 5 of plunger just breaks away from oil extraction flow groove, enter mechanical close release of pressure district, the introducing in the oil suction flow groove of the oil drain quantity of the trace in the release of pressure process and fluid volumetric expansion amount by vibration damping groove (hole).The fluid of oil cylinder 5 in the choke-out district is subjected to the volume of mechanical compress to account for the boost 20-30% of required compression total volume of fluid.Thrust plate of the present invention is characterised in that, from oil suction flow chute 11 to the mispairing angle φ the oil extraction flow groove 15
0Identical deflection direction and the turning to on the contrary of rotor 6 of deflection direction from oil extraction flow groove 15 to the mispairing angle the oil suction flow groove 11 with turning to of rotor 6, be-φ
0, mispairing angle φ
0Span be: 3 °≤φ
0≤ 7 °.
As shown in Figure 1, rotating shaft 1 drives rotor 6 and rotates in the counterclockwise direction, a group oil cylinder 5 setting-ins plunger 7 on the rotor 6, plunger 7 holds out against swash plate 9 by spring and oil pressure by crawler shoe 8, along with rotor 6 rotations, crawler shoe 8 slides along swash plate 9 surfaces, the oil cylinder 5 of plunger 7 slides on thrust plate 4, when plunger 7 relative cylinder bodies were overhanging, the bottom of plunger 7 increased with respect to the space between the oil cylinder 5, realized the oil suction stroke, plunger 7 relative cylinder bodies reach after top dead center outward, change the lower position among Fig. 1 over to, swash plate 9 forces in the plunger 7 relative cylinder bodies and contracts, and the space between the bottom of plunger 7 and the oil cylinder 5 dwindles, realize the oil extraction stroke, in plunger 7, contract, transfer to overhangingly, enter the oil suction stroke to after bottom dead center.Variable piston 10 in the pump bottom moves up and down, and changes hectare angle of swash plate 9, thereby regulates the discharge capacity of oil pump.Projection when the projection 13,13 of the oily window of oil cylinder 5 on thrust plate 4 ' be oil cylinder 5 enters the initial position in choke-out press area and choke-out release of pressure district, thrust plate 4 usefulness positioning pin holes 16 and locating stud 3 are fixed on the pump housing 2.
When plunger 7 was in the oil suction stroke, oil cylinder 5 sucked fluid by oil suction flow groove 11, and when plunger 7 was in the oil extraction stroke, oil cylinder 5 entered pressure duct by oil extraction flow groove 15 with fluid.Oil cylinder 5 breaks away from oil suction flow grooves 11 and is projected as 13 when entering press area on thrust plate 4, oil cylinder 5 windows are spaced apart plane 12 sealings, along with plunger 7 continues rotation with rotor 6, because the mechanical compress effect of sealing, by vibration damping groove (hole) 14 high pressure oil in the oil extraction flow groove 15 is introduced in the oil cylinder 5, make original low pressure oil volume compression in the oil cylinder 5, pressure raises, the edge that goes to the leading edge camber line of oily window projection 13 of its oil cylinder 5 and oil extraction flow groove 15 up to plunger 7 is tangent, oil pressure in the oil cylinder 5 rises to oil extraction pressure, when plunger 7 continues to rotate to oil cylinder 5 with 15 connections of oil extraction flow groove, oil pressure in the oil cylinder 5 equates with oil pressure in the oil extraction flow groove 15, can not produce flow and impact.When the oil extraction stroke of plunger 7 does not finish, when to be plunger 7 with rotor 6 rotate to position before the lower dead centre, the window of oil cylinder 5 just is separated with oil extraction flow groove 15, this moment oil cylinder 5 the position of projection of window 13 ' locate, plunger 7 is proceeded the oil extraction stroke with rotor 6 rotations, oil extraction discharge capacity that it is micro-and the fluid swell increment in the oil cylinder 5 are by in vibration damping groove 14 ' introducing oil suction flow groove 11, up to the edge of the leading edge camber line of the projection of the window of oil cylinder 5 and oil suction flow groove 11 when tangent, oil pressure in the oil cylinder 5 is reduced to oil suction pressure by oil extraction pressure, therefore can not produce flow and impact.Because the fluid in the oil cylinder 5 is not having the mechanical swelling process of sealing by oil extraction flow groove 15 in the release of pressure process of oil suction flow groove 11, no matter so in normal desirable operating mode or disturbed under the operating mode by load, former thereby generation addition of vacuum degree and initiation air pocket all can not occur, produce noise because of flow.
Fig. 4 is the geometrical construction figure of thrust plate 4 of the present invention, Y-Y ' axle among the figure is the line of plunger 7 at two dead points of oil extraction stroke and oil suction stroke, be called the dead point axle, ON is the bisector of the circumferential cornerite from oil suction flow groove 11 to the plane, interval 12 the oil extraction flow groove 15, ON ' be from oil extraction flow groove 15 to the plane, interval 12 the oil suction flow groove 11 ' the bisector of circumferential cornerite, be the sense of rotation of rotor 6 counterclockwise among the figure, be taken as the postive direction of angle, ON, ON ' is called the mispairing angle with the angle of dead point axle Y-Y ', wherein the folded last mispairing angle of ON and Y-Y ' axle is deflection counterclockwise, for on the occasion of, be designated as φ
0, the folded following mispairing angle of ON ' and Y-Y ' axle is clockwise direction deflection, is negative value, is designated as-φ
0:
φ
0Span be 3 °≤φ
0≤ 7 °;
Two at interval plane 12,12 ' circumferential cornerite equal the circumferential cornerite and the choke-out angle △ φ sum of the projection of window on thrust plate 4 of oil cylinder 5, for the concrete structure of zero lap degree, vibration damping groove (hole) 14,14 ' circumferential cornerite equal the choke-out angle.The circumferential cornerite of oil extraction flow groove 15 is less than the circumferential cornerite of oil suction flow groove 11.
The most preferred embodiment of thrust plate 4 of the present invention is mispairing angle φ
0=5 °.From oil extraction flow groove 15 is clockwise deflection φ to the mispairing angle of oil suction flow groove 11 counterclockwise
0, promptly-5 °.
The present invention is through experimental verification, make the rotor running stable by eliminating the air pocket vibration, improved volumetric efficiency, the scope of the zone of high pressure of mating part has reduced 1/10th, improved the balance quality of rotor, and reduced the specific pressure of flow face and [PV] value, and improved the wear resistance of thrust plate, can make improve 50% the working life of mating part; In the noise contrast test of axial piston pump, assignment method of the present invention and thrust plate move under declared working condition, can make the noise decline 6-10dB(A of pump).
Claims (3)
1, a kind of assignment method of low-noise axial plunger pump, the oil cylinder of plunger periodically slips over two flow grooves on thrust plate, the invention is characterized in, the geometric distribution of two flow grooves adopts non-symmetry structure, be the cornerite of the cornerite of oil extraction flow groove less than oil suction flow groove, the oil extraction stroke of plunger is not finished, the oil cylinder of plunger just breaks away from oil extraction flow groove, enter mechanical close release of pressure district, the mechanical compress oil drain quantity of trace and high-voltage oil liquid volumetric expansion amount are introduced in the oil suction flow groove by vibration damping groove (hole) in the release of pressure process.
2, by the described assignment method of claim 1, an oil suction flow groove 11 and an oil extraction flow groove 15 are arranged on thrust plate 4, have in the end of oil suction flow groove 11 and oil extraction flow groove 15 respectively in the counterclockwise direction vibration damping groove (hole) 14,14 ', the oil cylinder of plunger 7 cycle ground, garden at thrust plate upper edge flow groove 11,15 places under the drive of rotor 6 slides, the structure characteristic of thrust plate of the present invention is, from oil suction flow groove 11 to the mispairing angle φ the oil extraction flow groove 15
0Deflection direction identical with turning to of rotor 6, the deflection direction from oil extraction flow groove 15 to the mispairing angle the oil suction flow groove 11 and the switched in opposite of rotor 6 are-φ
0
3, by the described port plate structure of claim 2, it is characterized in that mispairing angle φ
0Span be: 3 °≤φ
0≤ 7 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 91111998 CN1025754C (en) | 1991-12-30 | 1991-12-30 | Valving method for low-noise axial plunger pump and valve plate structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 91111998 CN1025754C (en) | 1991-12-30 | 1991-12-30 | Valving method for low-noise axial plunger pump and valve plate structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1074019A true CN1074019A (en) | 1993-07-07 |
| CN1025754C CN1025754C (en) | 1994-08-24 |
Family
ID=4910957
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 91111998 Expired - Fee Related CN1025754C (en) | 1991-12-30 | 1991-12-30 | Valving method for low-noise axial plunger pump and valve plate structure |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1025754C (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1293305C (en) * | 2003-11-12 | 2007-01-03 | 浙江大学 | Bubble evolution proof plunger pump port plate |
| CN100447410C (en) * | 2003-09-17 | 2008-12-31 | Ts株式会社 | Axial piston hydraulic pump motor |
| CN101858339A (en) * | 2010-06-08 | 2010-10-13 | 太原理工大学 | Multi-oil discharge outlet axial plunger hydraulic pump |
| CN101892978A (en) * | 2010-07-28 | 2010-11-24 | 北京航空航天大学 | Valve plate structure for plunger pump |
| CN102155372A (en) * | 2011-04-11 | 2011-08-17 | 浙江大学 | Low-noise axial plunger pump based on average pressure |
| CN101694211B (en) * | 2009-10-16 | 2012-06-13 | 华中科技大学 | Port plate for plunger pump |
| CN102812244A (en) * | 2010-03-18 | 2012-12-05 | 株式会社小松制作所 | Hydraulic pump/motor and method for preventing pulsation of hydraulic pump/motor |
| CN103256007A (en) * | 2013-05-24 | 2013-08-21 | 中国石油大学(北京) | Underground dynamic pressurizing drilling rig |
| CN106368811A (en) * | 2016-08-26 | 2017-02-01 | 北京理工大学 | Valve plate and hydraulic output mechanism for engine and engine |
| CN107514359A (en) * | 2017-10-25 | 2017-12-26 | 青岛力克川液压机械有限公司 | A kind of inclined plate of variable piston pump structure |
| CN108026904A (en) * | 2015-09-16 | 2018-05-11 | Ｋｙｂ株式会社 | Hydraulic rotating machinery and its valve plate |
| CN108119322A (en) * | 2017-11-08 | 2018-06-05 | 哈尔滨理工大学 | A kind of New Type Valve Plate for balancing tilting moment |
| CN113339250A (en) * | 2021-06-30 | 2021-09-03 | 北京航空航天大学宁波创新研究院 | Plunger pump rotor oil window wrap angle detection method |
-
1991
- 1991-12-30 CN CN 91111998 patent/CN1025754C/en not_active Expired - Fee Related
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100447410C (en) * | 2003-09-17 | 2008-12-31 | Ts株式会社 | Axial piston hydraulic pump motor |
| CN1293305C (en) * | 2003-11-12 | 2007-01-03 | 浙江大学 | Bubble evolution proof plunger pump port plate |
| CN101694211B (en) * | 2009-10-16 | 2012-06-13 | 华中科技大学 | Port plate for plunger pump |
| CN102812244B (en) * | 2010-03-18 | 2015-04-15 | 株式会社小松制作所 | Hydraulic pump/motor and method for preventing pulsation of hydraulic pump/motor |
| CN102812244A (en) * | 2010-03-18 | 2012-12-05 | 株式会社小松制作所 | Hydraulic pump/motor and method for preventing pulsation of hydraulic pump/motor |
| US9097113B2 (en) | 2010-03-18 | 2015-08-04 | Komatsu Ltd. | Hydraulic pump/motor and method of suppressing pulsation of hydraulic pump/motor |
| CN101858339A (en) * | 2010-06-08 | 2010-10-13 | 太原理工大学 | Multi-oil discharge outlet axial plunger hydraulic pump |
| CN101858339B (en) * | 2010-06-08 | 2014-07-30 | 太原理工大学 | Multi-oil discharge outlet axial plunger hydraulic pump |
| CN101892978A (en) * | 2010-07-28 | 2010-11-24 | 北京航空航天大学 | Valve plate structure for plunger pump |
| CN102155372A (en) * | 2011-04-11 | 2011-08-17 | 浙江大学 | Low-noise axial plunger pump based on average pressure |
| CN103256007A (en) * | 2013-05-24 | 2013-08-21 | 中国石油大学(北京) | Underground dynamic pressurizing drilling rig |
| CN108026904A (en) * | 2015-09-16 | 2018-05-11 | Ｋｙｂ株式会社 | Hydraulic rotating machinery and its valve plate |
| CN106368811A (en) * | 2016-08-26 | 2017-02-01 | 北京理工大学 | Valve plate and hydraulic output mechanism for engine and engine |
| CN106368811B (en) * | 2016-08-26 | 2019-01-18 | 北京理工大学 | A kind of valve plate, hydraulic output mechanism and engine for engine |
| CN107514359A (en) * | 2017-10-25 | 2017-12-26 | 青岛力克川液压机械有限公司 | A kind of inclined plate of variable piston pump structure |
| CN108119322A (en) * | 2017-11-08 | 2018-06-05 | 哈尔滨理工大学 | A kind of New Type Valve Plate for balancing tilting moment |
| CN108119322B (en) * | 2017-11-08 | 2019-07-26 | 哈尔滨理工大学 | A kind of valve plate balancing tilting moment |
| CN113339250A (en) * | 2021-06-30 | 2021-09-03 | 北京航空航天大学宁波创新研究院 | Plunger pump rotor oil window wrap angle detection method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1025754C (en) | 1994-08-24 |
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