CN102628443A - Magnetic force compensating type axial flow-distribution radial plunger pump - Google Patents
Magnetic force compensating type axial flow-distribution radial plunger pump Download PDFInfo
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- CN102628443A CN102628443A CN2011101653656A CN201110165365A CN102628443A CN 102628443 A CN102628443 A CN 102628443A CN 2011101653656 A CN2011101653656 A CN 2011101653656A CN 201110165365 A CN201110165365 A CN 201110165365A CN 102628443 A CN102628443 A CN 102628443A
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- circular arc
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- pintle
- cylinder body
- plunger pump
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Abstract
The invention provides a magnetic force compensating type axial flow-distribution radial plunger pump. A first pair of circular arc permanent magnets (5a, 5b) is mounted at the right end of an inner hole of a cylinder body (8) matched with a flow distribution shaft; a second pair of circular arc permanent magnets (9a, 9b) is symmetrically mounted at the left end of the inner hole; a first pair of circular arc electromagnets (6a, 6b) and a second pair of circular arc electromagnets (13a, 13b) are symmetrically mounted in corresponding positions on the flow distribution shaft (15); two piezoelectric crystal pressure sensors (12a, 12b) are symmetrically mounted in high pressure and low pressure regions at the supporting surface of the external surface of the flow distribution shaft (15); the signal output ends of the piezoelectric crystal pressure sensors are respectively connected with an adjusting control unit (17); the output end of the adjusting control unit (17) is respectively connected with two power amplifiers (16a, 16b); the output ends of the two power amplifiers (16a, 16b) are respectively connected with the first pair of circular arc electromagnets (6a, 6b) and the second pair of circular arc electromagnets (13a, 13b).
Description
Technical field
The present invention relates to the radial plunger pump in the hydraulic element, relate in particular to the axle flow type radial plunger pump of aqueous medium or high-pressure high-flow oil medium.
Background technique
Pintle is one of crucial component part of flow radial plunger pump (or motor), and its effect comprises the turnover that distributes high low pressure fluid (or water), bears the eccentric load of cylinder body.Owing to there is very big speed of related movement between cylinder body and the pintle, if specific contact pressure is very big again, wearing and tearing will be very serious, directly affect pump performance and life-span.For making oil (or water) film thickness that had both kept certain between cylinder body and the pintle that dry friction not take place, can not cause leaking the excessive volumetric efficiency that reduces pump because of the excesssive gap between the two again, adopt the residual clamping force design method usually.The residual clamping force design method is introduced high pressure oil (or water) exactly between friction pair, lean on the static balance of its generation to fall most of impacting force, and cylinder body relies on remaining impacting force to be pressed onto on the pintle.The thrust load amplitude of variation suffered owing to cylinder body is very big; So it is very little that residual clamping force can not be got; This just causes usually can not form effective supporting oil (or water) film between the friction pair; Liquid friction and dry friction exist simultaneously, and lubrication circumstances will be looked residual clamping force size, equalising torque quality, suface processing quality, relative velocity height and oil (or water) film-strength size and decided.Because residual clamping force can not initiatively be controlled according to operating mode; So the lubrication circumstances between the friction pair is uncertain, look operating mode fully and decide, and owing to the reasons such as variation, accuracy of manufacturing and alignment error of load; The suffered hydraulic coupling of pintle also can not reach balance fully; Often occur eccentric wear between friction pair, cause and leak and " seize " problem, make that the volumetric efficiency of pump and life-span are all had a strong impact on.
The noise of axle flow radial plunger pump is mainly derived from the flow distributing noise of pintle; Though taked picture that many measures such as balance oil groove are set on thrust plate; But because the uncontrollability of oil film or water film thickness, work condition environment changes or can not guarantee the thickness of best oil film or moisture film during the parameter perturbation, this has just caused the uncontrollability of noise.
The problems referred to above performance in high-pressure large-displacement oil dielectric fluid press pump is outstanding especially, and compares oily medium, and water (pure water or seawater) medium greasy property is poor; Viscosity low (be about oil 1/40), the leakage of same interstitial water is much more serious than oil, is the volumetric efficiency of assurance pump; Can only further reduce the gap between the friction pair; This makes can not set up oil film or the moisture film with effective rigidity between friction pair, be difficult to produce enough supporting forces, also more is difficult to adapt to the variation of load; Even adopt high-abrasive material also to be difficult to reach the volumetric efficiency and the life-span of expection, make it become one of technical bottleneck of oil hydraulic pump.
Summary of the invention
Purpose of the present invention is to make cylinder body be in Optimum Lubrication; Avoid because various factors causes cylinder body-pintle friction pair oil film or moisture film to destroy; And then cylinder body that causes and the dry friction between pintle, improve the working life and the volumetric efficiency of pump, effectively reduce the noise of pump.
The present invention is a kind of magnetic compensation formula axle flow radial plunger pump; The left end of rotating shaft 1 is installed on the bearing 3; And be connected with cylinder body 8 through coupling 4; Pintle 15 left ends are installed in the endoporus of housing 11, and cylinder body 8 is sleeved on the right-hand member of pintle 15, and the right-hand member of the endoporus that cooperates with pintle at cylinder body 8 is installed first couple of circular arc permanent magnet 5a, 5b; The left end symmetry is installed second couple of circular arc permanent magnet 9a, 9b; Be symmetrically installed with first couple of circular arc electromagnet 6a, 6b, the second couple of circular arc electromagnet 13a, 13b in pintle 15 corresponding positions, high pressure on pintle 15 appearance supporting surfaces and low pressure area symmetry are equipped with two piezoelectric crystal pressure transducer 12a, 12b, its signal output part respectively with regulate control unit 17 and be connected; The output terminal of regulating control unit 17 is connected with two power amplifier 16a, 16b respectively, and the output terminal of two power amplifier 16a, 16b is connected with first couple of circular arc electromagnet 6a, 6b, second couple of circular arc electromagnet 13a, 13b respectively.
The present invention compares with background technique; The beneficial effect that has is: the electromagnetic force of utilizing close-loop controlled; Uncontrollable oil film or moisture film supporting force in the cylinder body of compensated pump between survey and the pintle realize the active closed loop control of best oil film of cylinder body-pintle friction pair or water film thickness, make cylinder body be in Optimum Lubrication; Improve oil hydraulic pump working life of aqueous medium oil hydraulic pump particularly, effectively reduced the noise of pump; Avoided owing to pintle receives cylinder body and pintle this eccentric wear and " seize " problem to friction pair that uneven hydraulic coupling causes; Volumetric efficiency, reliability and the working life of pump are improved, a pressure of flow radial plunger pump is further enhanced.
Description of drawings
Fig. 1 is a structural representation of the present invention, and Fig. 2 is the A-A sectional view of Fig. 1, and reference character and corresponding name are called: rotating shaft 1, pump cover 2, bearing 3; 4, the first pairs of circular arc permanent magnets of coupling 5a, 5b, the second couple of circular arc permanent magnet 9a, 9b, the first couple of circular arc electromagnet 6a, 6b, the second couple of circular arc electromagnet 13a, 13b; Plunger 7, cylinder body 8, oil outlet 10, housing 11, the first piezoelectric crystal pressure transducer 12a; The second piezoelectric crystal pressure transducer 12b, cable seal 14a, 14b, 14c, pintle 15, the first power amplifier 16a, the second power amplifier 16b; Regulate control unit 17, filler opening 18, stator 19, screw 20.
Embodiment
Like Fig. 1, shown in Figure 2; The present invention is a kind of magnetic compensation formula axle flow radial plunger pump; The left end of rotating shaft 1 is installed on the bearing 3; And be connected with cylinder body 8 through coupling 4; Pintle 15 left ends are installed in the endoporus of housing 11, and cylinder body 8 is sleeved on the right-hand member of pintle 15, and the right-hand member of the endoporus that cooperates with pintle at cylinder body 8 is installed first couple of circular arc permanent magnet 5a, 5b; The left end symmetry is installed second couple of circular arc permanent magnet 9a, 9b; Be symmetrically installed with first couple of circular arc electromagnet 6a, 6b, the second couple of circular arc electromagnet 13a, 13b in pintle 15 corresponding positions, high pressure on pintle 15 appearance supporting surfaces and low pressure area symmetry are equipped with two piezoelectric crystal pressure transducer 12a, 12b, its signal output part respectively with regulate control unit 17 and be connected; The output terminal of regulating control unit 17 is connected with two power amplifier 16a, 16b respectively, and the output terminal of two power amplifier 16a, 16b is connected with first couple of circular arc electromagnet 6a, 6b, second couple of circular arc electromagnet 13a, 13b respectively.
Like Fig. 1, shown in Figure 2, the polarity of first couple of circular arc electromagnet 6a of the first couple of circular arc permanent magnet 5a, 5b, the second couple of circular arc permanent magnet 9a, 9b and corresponding position, 6b, the second couple of circular arc electromagnet 13a, 13b is identical.
First couple of circular arc electromagnet 6a, 6b, second couple of circular arc electromagnet 13a, 13b are installed on the pintle 15 through screw 20 respectively.
First couple of circular arc permanent magnet 5a, 5b, second couple of circular arc permanent magnet 9a, 9b are installed on the endoporus of cylinder body 8 through screw respectively.
The regulon 17 and the first power amplifier 16a, the second power amplifier 16b are installed on the housing 11, or are installed in outside the housing 11.
First pair of circular arc electromagnet 6a, 6b, second pair of circular arc electromagnet 13a, the actuating cable of 13b and the signal cable of the first piezoelectric crystal pressure transducer 12a, the second piezoelectric crystal pressure transducer 12b are connected with the first power amplifier 16a, the second power amplifier 16b with regulon 17 through the aperture on the pintle, filler opening 18 and oil outlet 10 respectively, and aperture outlet port 14a, 14b, 14c carry out cable seal.
Regulating control unit 17 can be by microcontroller, or analog circut constitutes; Regulate control unit 17 and earlier the pressure signal that the first piezoelectric crystal pressure transducer 12a, second piezoelectric crystal pressure transducer 12b feedback are come is carried out filtering, amplification and linearization; Compare to such an extent that deviate with setting value again; Through control strategy deviation is carried out computing; And then produce control signal control current of electromagnet, the active closed loop control of best oil film or water film thickness between realization cylinder body-thrust plate friction pair.
Working procedure of the present invention is following:
Cylinder body 8 rotates under the driving of rotating shaft 1; The power that cylinder body 8 receives in operation process comprises: plunger 7 acts on the positive pressure on the cylinder body 8; The supporting force of the pressure field between the supporting force of rotating shaft 1, pintle 15 and the cylinder body 8; The supporting force that comprises oil film or moisture film; The supporting force of pintle 17 surface bearing faces, the magnetic repulsion between first pair of circular arc permanent magnet of permanent magnet 5a, 5b, the second couple of circular arc permanent magnet 9a, 9b and the first couple of circular arc electromagnet 6a, 6b, the second couple of circular arc electromagnet 13a, the 13b.Magnetic repulsion in above-mentioned all power between permanent magnet and electromagnet was controlled, other power was all uncontrollable.Be installed in the first piezoelectric crystal pressure transducer 12a on the pintle, the pressure that the second piezoelectric crystal pressure transducer 12b experiences the pintle both sides respectively; This pressure signal is given through signal cable and is regulated control unit 17; Regulate control unit 17 and calculate pintle 15 and the cylinder body 8 interior gap situations of change of surveying in view of the above; Whether have the pintle eccentric wear to take place, this pressure signal and optimum setting value simultaneously, produce controlled quentity controlled variable through control algorithm if relatively producing deviation; By the first power amplifier 16a, the second power amplifier 16b control signal is carried out the power amplification DM; Compensation realizes best oil film of cylinder body-pintle friction pair or water film thickness because the gap of surveying in pintle that working conditions change causes and the cylinder body changes, and makes cylinder body be in Optimum Lubrication.
The heat that electromagnet sends can be taken away by the recycle oil between pintle and the cylinder body (or water), and the hydraulic damping that oil film between pintle and the cylinder body or moisture film form can replenish controlled magnetic repulsion underdamping problem, makes control performance further improve.
Claims (5)
1. magnetic compensation formula axle flow radial plunger pump; The left end of rotating shaft (1) is installed on the bearing (3); And be connected with cylinder body (8) through coupling (4); Pintle (15) left end is installed in the endoporus of housing (11); Cylinder body (8) is sleeved on the right-hand member of pintle (15), it is characterized in that, the right-hand member of the endoporus that cooperates with pintle at cylinder body (8) is installed first pair of circular arc permanent magnet (5a, 5b); The left end symmetry is installed second pair of circular arc permanent magnet (9a, 9b); Be symmetrically installed with first pair of circular arc electromagnet (6a, 6b), second pair of circular arc electromagnet (13a, 13b) in the corresponding position of pintle (15), high pressure on pintle (15) appearance supporting surface and low pressure area symmetry are equipped with two piezoelectric crystal pressure transducers (12a, 12b), and its signal output part is connected with adjusting control unit (17) respectively; The output terminal of regulating control unit (17) is connected with two power amplifiers (16a, 16b) respectively, and the output terminal of two power amplifiers (16a, 16b) is connected with first pair of circular arc electromagnet (6a, 6b), second pair of circular arc electromagnet (13a, 13b) respectively.
2. magnetic compensation formula axle flow radial plunger pump according to claim 1; It is characterized in that first pair of circular arc electromagnet (6a, 6b) of first pair of circular arc permanent magnet (5a, 5b), second pair of circular arc permanent magnet (9a, 9b) and corresponding position, the polarity of second pair of circular arc electromagnet (13a, 13b) are identical.
3. magnetic compensation formula axle flow radial plunger pump according to claim 1 is characterized in that regulon (17) and first power amplifier (16a), second power amplifier (16b) are installed on the housing (11), or are installed in outside the housing (11).
4. magnetic compensation formula axle flow radial plunger pump according to claim 1; It is characterized in that; The signal cable of the actuating cable of first pair of circular arc electromagnet (6a, 6b), second pair of circular arc electromagnet (13a, 13b) and the first piezoelectric crystal pressure transducer (12a), the second piezoelectric crystal pressure transducer (12b) is connected with first power amplifier (16a), second power amplifier (16b) with regulon (17) through the aperture on the pintle, filler opening (18) and oil outlet (10) respectively, and aperture outlet port (14a, 14b, 14c) carries out cable seal.
5. magnetic compensation formula axle flow radial plunger pump according to claim 1 is characterized in that, regulating control unit (17) can be by microcontroller, or analog circut constitutes; Regulate control unit (17) and earlier the pressure signal that the first piezoelectric crystal pressure transducer (12a), the second piezoelectric crystal pressure transducer (12b) feedback are come is carried out filtering, amplification and linearization; Compare to such an extent that deviate with setting value again; Through control strategy deviation is carried out computing; And then produce control signal control current of electromagnet, the active closed loop control of best oil film or water film thickness between realization cylinder body-thrust plate friction pair.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101653656A CN102628443A (en) | 2011-06-14 | 2011-06-14 | Magnetic force compensating type axial flow-distribution radial plunger pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101653656A CN102628443A (en) | 2011-06-14 | 2011-06-14 | Magnetic force compensating type axial flow-distribution radial plunger pump |
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| CN102628443A true CN102628443A (en) | 2012-08-08 |
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| CN2011101653656A Pending CN102628443A (en) | 2011-06-14 | 2011-06-14 | Magnetic force compensating type axial flow-distribution radial plunger pump |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103410655A (en) * | 2013-08-18 | 2013-11-27 | 北京工业大学 | Flow distribution pair clearance magnetic force compensation-type water hydraulic motor |
| CN107269520A (en) * | 2017-07-17 | 2017-10-20 | 常州大学 | Magnetic compensation floating side plate sub-assembly |
| CN109973385A (en) * | 2019-04-18 | 2019-07-05 | 兰州理工大学 | A kind of gear pump in magnetic compensation floating side plate gap |
| CN113623163A (en) * | 2021-09-22 | 2021-11-09 | 哈尔滨工业大学 | End face flow distribution axial plunger pump based on liquid-magnetic composite support |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1453472A (en) * | 2003-06-02 | 2003-11-05 | 江苏大学 | Axial-flow radial plunger pump with floating bush sleeve |
| CN1683789A (en) * | 2004-12-09 | 2005-10-19 | 兰州理工大学 | Double action radial plunger pump |
| CN1847649A (en) * | 2005-10-28 | 2006-10-18 | 兰州理工大学 | Oil film thickness controlling system for end fluid-distributing axial plunger pump |
| CN201133329Y (en) * | 2007-10-16 | 2008-10-15 | 董桂敏 | Constant pressure variable radial piston pump |
| US20090007773A1 (en) * | 2006-03-14 | 2009-01-08 | Raphael Zhu | Axial plunger pump or motor |
-
2011
- 2011-06-14 CN CN2011101653656A patent/CN102628443A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1453472A (en) * | 2003-06-02 | 2003-11-05 | 江苏大学 | Axial-flow radial plunger pump with floating bush sleeve |
| CN1683789A (en) * | 2004-12-09 | 2005-10-19 | 兰州理工大学 | Double action radial plunger pump |
| CN1847649A (en) * | 2005-10-28 | 2006-10-18 | 兰州理工大学 | Oil film thickness controlling system for end fluid-distributing axial plunger pump |
| US20090007773A1 (en) * | 2006-03-14 | 2009-01-08 | Raphael Zhu | Axial plunger pump or motor |
| CN201133329Y (en) * | 2007-10-16 | 2008-10-15 | 董桂敏 | Constant pressure variable radial piston pump |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103410655A (en) * | 2013-08-18 | 2013-11-27 | 北京工业大学 | Flow distribution pair clearance magnetic force compensation-type water hydraulic motor |
| CN103410655B (en) * | 2013-08-18 | 2016-04-13 | 北京工业大学 | A kind of flow distribution pair clearance magnetic force compensation-type water hydraulic motor |
| CN107269520A (en) * | 2017-07-17 | 2017-10-20 | 常州大学 | Magnetic compensation floating side plate sub-assembly |
| CN107269520B (en) * | 2017-07-17 | 2019-01-29 | 常州大学 | Magnetic compensation floating side plate sub-assembly |
| CN109973385A (en) * | 2019-04-18 | 2019-07-05 | 兰州理工大学 | A kind of gear pump in magnetic compensation floating side plate gap |
| CN113623163A (en) * | 2021-09-22 | 2021-11-09 | 哈尔滨工业大学 | End face flow distribution axial plunger pump based on liquid-magnetic composite support |
| CN113623163B (en) * | 2021-09-22 | 2022-07-05 | 哈尔滨工业大学 | End face flow distribution axial plunger pump based on liquid-magnetic composite support |
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Application publication date: 20120808 |