CN1293305C - Bubble evolution proof plunger pump port plate - Google Patents
Bubble evolution proof plunger pump port plate Download PDFInfo
- Publication number
- CN1293305C CN1293305C CNB2003101086694A CN200310108669A CN1293305C CN 1293305 C CN1293305 C CN 1293305C CN B2003101086694 A CNB2003101086694 A CN B2003101086694A CN 200310108669 A CN200310108669 A CN 200310108669A CN 1293305 C CN1293305 C CN 1293305C
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- Prior art keywords
- plunger
- damping slot
- groove
- plunger pump
- damping groove
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- 238000013016 damping Methods 0.000 claims abstract description 57
- 210000003734 kidney Anatomy 0.000 claims description 7
- 230000010349 pulsation Effects 0.000 abstract description 7
- 238000000926 separation method Methods 0.000 abstract description 2
- 238000010521 absorption reaction Methods 0.000 abstract 3
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 230000002708 enhancing effect Effects 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 4
- 230000035939 shock Effects 0.000 description 4
- 238000004458 analytical method Methods 0.000 description 2
- 239000012141 concentrate Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000011218 segmentation Effects 0.000 description 1
- 230000008961 swelling Effects 0.000 description 1
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- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
The present invention discloses a bubble evolution preventing plunger pump distributing disk. A low-pressure side damping groove of the distributing disk is formed by combining a first equal cross-section damping groove and a second equal cross-section damping groove, wherein a central angle of the first equal cross-section damping groove is equal to an included angle of the connecting lines of a waist-shaped hole central line on a cylinder body, and an upper dead point and a lower dead point of the distributing disk. The low-pressure side damping groove is provided with a two-stage throttling structure, and the two-stage throttling structure can prevent the evolution of bubbles occurring when a plunger working chamber and a low-pressure oil groove are switched on. When a plunger outward extends and absorbs oil, the possibility of the occurrence of gas cavity because of hard oil absorption is avoided because the area of the passage of the damping groove with the combined structure is large, and the resistance loss of the damping groove is very small. Therefore, the bubbles in an oil absorption groove and the plunger chamber are greatly decreased, and the gas cavity noise and the pump flow pulsation of a pump occurring in a high pressure area are greatly reduced. The bubble evolution preventing plunger pump distributing disk suppresses the evolution of the bubbles by enhancing the pressure of a stream separation point, and the bubble evolution preventing plunger pump distributing disk can obviously reduce the noise of the plunger pump and enhance the quality of flow when the oil absorption groove is provided with a segmenting equal cross-section damping groove.
Description
Technical field
The present invention relates to a kind of thrust plate, relate in particular to the plunger pump thrust plate that a kind of anti-bubble is separated out.
Background technique
The noise of plunger pump, the main cause of vibration compression shock, flow that to be plunger cavity occur in the high and low pressure oil groove of thrust plate switches pour in down a chimney, air pocket etc.The work of the noise of plunger pump reduction for a long time concentrates on following three aspects: the one, improve thrust plate damping slot structure, and reduce compression shock, make plunger cavity transition stably from low pressure to the high pressure to reduce pressure peak; The 2nd, improve oil absorbency, reduce the oil suction resistance, air pocket appears when avoiding oil suction; The 3rd, reduce the crossing release of plunger active chamber dead volume and the air pocket that occurs, the domestic people of having has proposed a kind of improvement project of thrust plate, analysis points out that the plunger active chamber may become the main noise reason because of the air pocket vibration noise that the mistake release occurs, asymmetric arrangement by high low pressure oil groove on the thrust plate prevents the release of crossing of plunger active chamber, and his research paper report adopts new thrust plate to reduce because the air pocket vibration noise that the mistake release of plunger active chamber occurs.
Summary of the invention
Because air pocket appears at the moment of plunger cavity and low-pressure tank connection easily, owing to flow at high speed, fluid separates with wall and low pressure area occurs, very easily separates out at this regional bubble in damping slot.The purpose of this invention is to provide the plunger pump thrust plate that a kind of anti-bubble is separated out, be in thrust plate oil suction groove side, be provided with and have the prismatic damping slot structure of segmentation, when plunger cavity broke away from high-pressure trough, plunger cavity and low voltage side damping slot were connected, and continue to be compressed in a small angle inner plunger chamber, the fluid of discharging enters the oil suction groove through damping slot uniform section section, the damping slot of uniform section section can improve the pressure of point of flow separation as local resistance, prevents that bubble from separating out; In the overhanging oil suction of the plunger stage, it is big that the uniform section area of damping slot becomes, and plunger cavity oil suction resistance is very little, guarantees that oil suction is unobstructed.
Since the plunger active chamber with thrust plate on the moment pressure reduction connected of low-pressure tank bigger, the low pressure area that a fluid stream breaks away from wall, pressure drop can appear in damping slot, and separating out of bubble can appear rapidly in this low pressure area, because plunger pump oil suction groove pressure very low (about 0.16bar), the bubble of separating out can be grown up, can not vanished, and can not form Cavitation Noise in oil suction groove zone.Yet along with the oil-absorbing process of plunger cavity at the oil suction groove, these bubbles are inhaled into plunger cavity with fluid, along with cylinder body rotates to the zone of high pressure, plunger cavity and high pressure oil groove are connected, and fluid pours in down a chimney and enters plunger cavity, bubble in the plunger cavity is sharply crumbled and fall, cause Cavitation Noise, vibration, because vanishing of air pocket poured in down a chimney flow and increased, the pulsation of aggravation plunger pump output flow, thus cause that delivery quality degenerates.
The technical solution used in the present invention is: comprise that having high pressure oil groove, cross section is the thrust plate that triangle flaring high pressure side damping slot, oil suction groove, low voltage side damping slot are formed.Wherein the low voltage side damping slot is to be combined by the first uniform section damping slot and the second uniform section damping slot, and the central angle of the first uniform section damping slot equals the angle of lower dead centre line on kidney slot center line on the cylinder body and the thrust plate.
The useful effect that the present invention has is: constructed the two-step throttle structure on the low pressure damping slot, can prevent that the bubble of appearance was separated out when plunger active chamber and low-pressure tank from connecting; When the overhanging oil suction of plunger, because the damping slot area of passage of composite structure is big, drag losses is very little, has also avoided because the possibility of air pocket does not freely appear in oil suction.Therefore the bubble in oil suction groove and plunger cavity greatly reduces, and the Cavitation Noise that pump occurs in the zone of high pressure and the flow pulsation of pump greatly reduce.
Description of drawings
Fig. 1 is a port plate structure principle schematic of the present invention;
Fig. 2 is that the A-A of Fig. 1 analyses and observe partial enlarged drawing;
Fig. 3 is the local enlarged diagram of the G of Fig. 2.
Among the figure: 1. thrust plate, 2. high pressure oil groove, 3. high pressure side damping slot, the 4. kidney slot on the cylinder body, 5. oil suction groove, the 6. second uniform section damping slot, the 7. first uniform section damping slot, the 8. kidney slot on the cylinder body, 9. plunger, 10. cylinder body, 11. low voltage side damping slots, 12. plunger cavities.
Embodiment
As Fig. 1, Fig. 2, shown in Figure 3, the present invention includes and having high pressure oil groove 2, cross section is the thrust plate 1 that triangle flaring high pressure side damping slot 3, oil suction groove 5, low voltage side damping slot 11 are formed; Wherein low voltage side damping slot 11 is to be combined by the first uniform section damping slot 7 and the second uniform section damping slot 6, the central angle Δ of the first uniform section damping slot 7
3Equal the angle Δ of lower dead centre line YY ' on kidney slot center line on the cylinder body and the thrust plate
4
The cornerite MOB of oil suction groove 5 is greater than the cornerite POF of high pressure oil groove 2.
The central angle Δ of low voltage side damping slot 11
2Central angle Δ less than high pressure side damping slot 3
1
The degree of depth of the second uniform section damping slot 6 in the low voltage side damping slot 11 is greater than the degree of depth of the first uniform section damping slot 7.
In the plunger pump assignment process plunger active chamber by low pressure to the high pressure side transition and when connecting, can compression shock appear and flow pours in down a chimney, cause that the pulsation of plunger cavity internal pressure rapid change and oil hydraulic pump output flow strengthens, cause very big vibration and noise, have a strong impact on the quality of plunger pump.Big quantity research all concentrates on and reduces by the compression shock aspect of low pressure to high pressure.For the air pocket reason, people consider that the mistake improve the oil absorbency of pump and to avoid the plunger cavity closed volume is unloaded compression swelling and the air pocket that occurs.The present invention find plunger pump by high pressure in the process of low pressure conversion, because flow at high speed phenomenon and the defection of fluid walls emaciated face cause separating out of bubble, because the pressure of oil suction groove is very low in the pump, these bubbles are difficult for dissolving in the fluid, along with the overhanging oil suction of plunger enters plunger cavity, so plunger cavity contains the isolated bubble in oil suction district.In the high pressure side, high pressure oil impacts and enters plunger cavity, and the shattered to pieces meeting of bubble causes very big noise and vibration on the one hand, can aggravate the pulsation of POF simultaneously.And separating out with the shape relation of damping slot of this bubble is close.The present invention is based on discovery and experimental study result, proposed new port plate structure, avoid plunger pump separating out by the bubble of high pressure when low pressure is changed to this phenomenon, reduce pump noise, reduce the flow pulsation of pump.
Working procedure of the present invention is as follows:
The plunger active chamber breaks away from high pressure oil groove 2, to lower dead centre (the corresponding position of OY ' axle in as Fig. 1) motion, in the plunger cavity 12 be and the same high pressure of plunger pump outlet, when movement of cylinder block arrives the OE position (as shown in Figure 1), plunger cavity just in time break away from high pressure oil groove 2 and with low voltage side damping slot 11 in the contacting of the first uniform section damping slot 7 (as OD among Fig. 1), plunger cavity 12 is at Δ
4Be to be in to continue compressive state and carry out oil extraction in the angle, the fluid that plunger cavity 12 is discharged flows into 5 (as shown in Figure 3) of oil suction grooves through the second uniform section damping slot 6, the HI section of the first uniform section damping slot 7 has played drag effect, make fluid at the H point owing to the low pressure that fluid breakdown occurs is raise, avoided bubble to separate out and grow up, the raising of this resistance is relevant with the length of HI section, along with plunger cavity at Δ
4Interior pressure reduces, and this resistance also reduces.When cylinder body drive plunger cavity moved to OY ' axle, the overhanging oil-absorbing process of plunger 9 beginnings was because the central angle Δ of the first uniform section damping slot 7
3Equal the angle Δ of lower dead centre line YY ' on kidney slot 8 center lines on the cylinder body and the thrust plate
4So the second uniform section damping slot 6 is connected with the kidney slot 8 on the cylinder body, because the increase of flow area makes the oil suction resistance greatly reduce.Avoided the bubble in the plunger pump working procedure to separate out thus, so the noise of plunger pump greatly reduce, the output flow pulsation reduces with vibration.
Claims (4)
1. plunger pump thrust plate that anti-bubble is separated out comprises that having high pressure oil groove (2), cross section is the thrust plate (1) that triangle flaring high pressure side damping slot (3), oil suction groove (5), low voltage side damping slot (11) are formed; It is characterized in that: low voltage side damping slot (11) is to be combined central angle (the Δ of the first uniform section damping slot (7) by the first uniform section damping slot (7) and the second uniform section damping slot (6)
3) equal angle (the Δ of lower dead centre line on kidney slot (8) center line on the cylinder body and the thrust plate (YY ')
4).
2. the plunger pump thrust plate that a kind of anti-bubble according to claim 1 is separated out is characterized in that: the cornerite (MOB) of oil suction groove (5) is greater than the cornerite (POF) of high pressure oil groove (2).
3. the plunger pump thrust plate that a kind of anti-bubble according to claim 1 is separated out is characterized in that: central angle (the Δ of low voltage side damping slot (11)
2) less than central angle (the Δ of high pressure side damping slot (3)
1).
4. the plunger pump thrust plate that a kind of anti-bubble according to claim 1 is separated out is characterized in that: the degree of depth of the second uniform section damping slot (6) in the low voltage side damping slot (11) is greater than the degree of depth of the first uniform section damping slot (7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101086694A CN1293305C (en) | 2003-11-12 | 2003-11-12 | Bubble evolution proof plunger pump port plate |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101086694A CN1293305C (en) | 2003-11-12 | 2003-11-12 | Bubble evolution proof plunger pump port plate |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1544813A CN1544813A (en) | 2004-11-10 |
| CN1293305C true CN1293305C (en) | 2007-01-03 |
Family
ID=34334807
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003101086694A Expired - Fee Related CN1293305C (en) | 2003-11-12 | 2003-11-12 | Bubble evolution proof plunger pump port plate |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1293305C (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101225791B (en) * | 2008-01-04 | 2010-06-09 | 镇江大力液压马达有限责任公司 | Distributing plate of plane flow-distributing liquid-pressure motor and manufacturing method therefor |
| WO2011046351A2 (en) * | 2009-10-13 | 2011-04-21 | Kim Gi-Chan | Actuator using pneumatic pressure and hydraulic pressure |
| CN101694211B (en) * | 2009-10-16 | 2012-06-13 | 华中科技大学 | Port plate for plunger pump |
| CN101892978B (en) * | 2010-07-28 | 2012-07-04 | 北京航空航天大学 | Valve plate structure for plunger pump |
| CN102297131A (en) * | 2011-07-08 | 2011-12-28 | 兰州理工大学 | Port plate and hydraulic pump equipped with it |
| CN103486016A (en) * | 2013-09-16 | 2014-01-01 | 同济大学 | Valve plate for low-noise anti-cavitation plunger pump |
| CN103883510B (en) * | 2014-04-17 | 2016-04-13 | 哈尔滨工业大学 | A kind of thrust plate pressure buffer concentrated flow piezometric force characteristic experimental apparatus for testing |
| 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 |
| CN113339250B (en) * | 2021-06-30 | 2022-08-16 | 北京航空航天大学宁波创新研究院 | Plunger pump rotor oil window wrap angle detection method |
| CN114382690B (en) * | 2022-01-18 | 2024-05-24 | 中铁工程装备集团有限公司 | Plunger pump valve plate |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4034652A (en) * | 1975-03-06 | 1977-07-12 | Caterpillar Tractor Co. | Method and valve face configuration for reducing noise in a hydraulic pump |
| US4920856A (en) * | 1987-07-30 | 1990-05-01 | Brueninghaus Hydraulik Gmbh | Axial piston machine of the swashplate or bent axis type having slot control and pressure balancing passages |
| CN1074019A (en) * | 1991-12-30 | 1993-07-07 | 甘肃工业大学 | The assignment method of low-noise axial plunger pump and port plate structure |
| US5230274A (en) * | 1992-02-11 | 1993-07-27 | Vickers Incorporated | Variable displacement hydraulic pump with quiet timing |
| US5593285A (en) * | 1995-01-13 | 1997-01-14 | Caterpillar Inc. | Hydraulic axial piston unit with multiple valve plates |
| JP2000097146A (en) * | 1998-09-18 | 2000-04-04 | Hitachi Constr Mach Co Ltd | Piston pump |
| CN2436689Y (en) * | 2000-06-08 | 2001-06-27 | 崔勇达 | High-performance double-action hydraulic vane pump |
| JP2003065215A (en) * | 2001-08-22 | 2003-03-05 | Toshiba Mach Co Ltd | Piston pump motor |
| CN2672320Y (en) * | 2003-11-12 | 2005-01-19 | 浙江大学 | Asymmetric damping slot plunger pump flow distribution disk |
-
2003
- 2003-11-12 CN CNB2003101086694A patent/CN1293305C/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4034652A (en) * | 1975-03-06 | 1977-07-12 | Caterpillar Tractor Co. | Method and valve face configuration for reducing noise in a hydraulic pump |
| US4920856A (en) * | 1987-07-30 | 1990-05-01 | Brueninghaus Hydraulik Gmbh | Axial piston machine of the swashplate or bent axis type having slot control and pressure balancing passages |
| CN1074019A (en) * | 1991-12-30 | 1993-07-07 | 甘肃工业大学 | The assignment method of low-noise axial plunger pump and port plate structure |
| US5230274A (en) * | 1992-02-11 | 1993-07-27 | Vickers Incorporated | Variable displacement hydraulic pump with quiet timing |
| US5593285A (en) * | 1995-01-13 | 1997-01-14 | Caterpillar Inc. | Hydraulic axial piston unit with multiple valve plates |
| JP2000097146A (en) * | 1998-09-18 | 2000-04-04 | Hitachi Constr Mach Co Ltd | Piston pump |
| CN2436689Y (en) * | 2000-06-08 | 2001-06-27 | 崔勇达 | High-performance double-action hydraulic vane pump |
| JP2003065215A (en) * | 2001-08-22 | 2003-03-05 | Toshiba Mach Co Ltd | Piston pump motor |
| CN2672320Y (en) * | 2003-11-12 | 2005-01-19 | 浙江大学 | Asymmetric damping slot plunger pump flow distribution disk |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1544813A (en) | 2004-11-10 |
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| PB01 | Publication | ||
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| SE01 | Entry into force of request for substantive examination | ||
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070103 Termination date: 20101112 |