CN102207066A - Double-acting plunger pump - Google Patents
Double-acting plunger pump Download PDFInfo
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- CN102207066A CN102207066A CN2011101853084A CN201110185308A CN102207066A CN 102207066 A CN102207066 A CN 102207066A CN 2011101853084 A CN2011101853084 A CN 2011101853084A CN 201110185308 A CN201110185308 A CN 201110185308A CN 102207066 A CN102207066 A CN 102207066A
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Abstract
The invention discloses a double-acting plunger pump comprising a left hydraulic pump and a right hydraulic pump. The double-acting plunger pump is characterized in that the hydraulic pumps comprise a left hydraulic mechanism and a right hydraulic mechanism which are symmetrically arranged; a driving gear is arranged between the left hydraulic mechanism and the right hydraulic mechanism and is meshed with a driven gear; the actuation end of the driving gear is connected with a servo motor; the left hydraulic mechanism and the right hydraulic mechanism are connected with the driving gear and the driven gear by a crank connecting rod transmission mechanism; the oil outlets of the left hydraulic mechanism and the right hydraulic mechanism are respectively connected with an actuating mechanism by a check valve; and the oil return openings of the left hydraulic mechanism and the right hydraulic mechanism are respectively connected with an oil tank by the check valve. In the double-acting plunger pump, output flow can be subjected to constant-flow output, and the double-acting plunger pump has smaller friction and vibration, small noise pollution and a simple structure.
Description
Technical field
The present invention relates to a kind of hydraulic element, be specifically related to a kind of double-action plunger pump.
Background technique
At present in oil hydraulic pump, plunger pump has obtained extensive use with its simple working principle, its principle is: when the drive force plunger is reciprocating in the cylinder body plunger hole, the airtight work cavity volume generation volume-variation that plunger and cylinder body are formed, thereby realize suction, oil extraction process, plunger pump has the rated pressure height, compact structure, advantages such as efficient height and Flow-rate adjustment convenience.
Plunger pump can be divided into radial and axial type according to the different spread patterns of plunger in cylinder body.The plunger radial of radial plunger pump is arranged and is installed in the cylinder body, cylinder body is by prime mover driven rotary, so cylinder body is commonly referred to as rotor, plunger is close to stator inner wall by the effect of centrifugal force or low pressure oil, when rotor is done clockwise reversed turning, owing between rotor and the stator throw of eccentric is arranged, it is protruding when plunger passes through upper half, swept volume increases gradually in the oil cylinder, forms partial vacuum, therefore just the oilhole on lining from the inlet port oil suction of oil distributing shaft; When going to lower half, stator inner wall pushes back plunger, and in-oil cylinder working oil chamber diminishes gradually, hydraulic oil is flowed out to the pressure hydraulic fluid port of oil distributing shaft, and rotor returns and circles, and each oil suction of each oil cylinder, pressure oil are once, rotor constantly rotates, and just can finish oil transportation work continuously.The working principle of axial piston pump is: plunger is installed in the cylinder body, circular shaft evenly distributes vertically, cylinder body is by the transmission shaft driven rotary, the oil sucking window of fluid on oil distribution casing of being supplied with by low pressure fuel pump enters oil cylinder, one end of plunger is close on the swash plate, and oil distribution casing and swash plate all maintain static.When transmission shaft drives the oil cylinder rotation, under the effect of low pressure food tray, plunger is just done linear reciprocating motion in oil cylinder, when plunger stretches out from oil cylinder, suck low pressure oil through oil distribution casing, when plunger is compressed into oil cylinder by swash plate, the pressure oil window output high pressure oil on oil distribution casing, cylinder body whenever circles, each plunger back and forth movement once, finish oil suction oil extraction process one time, drive cylinder body as transmission shaft and turn round continuously, just pressure oil output constantly.
Plunger pump is very extensive in the application of industrial field, and particularly at high pressure and ultrahigh-pressure hydraulic transmission field, plunger pump is in occupation of the status that can not be substituted.But, flow pulse rate is the critical defect of traditional plunger pump greatly all the time, for example, traditional cam-type axial piston pump and cammingly radial plunger pump, though the stream pulsation rate is reduced, but too much plunger not only causes pump structure numerous and jumbled, and this method in theory just may not realize constant current output.For another example, the someone adopts many cam work travel speeds to be superposed to the method for a constant, has obtained theoretic constant current output plunger pump, if but also 4 or 8 multiple at least of the quantity of plunger quantity.In addition, even can make plunger pump realize constant current output in theory.But, cause the actual flow of pump still to have very important pulsation rate because cam curve and phase place unavoidably exist processing and assembly error.
Summary of the invention
Goal of the invention of the present invention provides a kind of double-action plunger pump, uses this structure, can realize the constant current output of output flow, rubs and shakes lessly, and noise pollution is little, and structure is also comparatively simple.
To achieve the above object of the invention, the technical solution used in the present invention is: a kind of double-action plunger pump, comprise left oil hydraulic pump and right oil hydraulic pump, described oil hydraulic pump comprises a symmetrically arranged left side, right hydraulic mechanism, a described left side, be provided with a driving gear between right hydraulic mechanism, be engaged with driven gear with described driving gear, described driving gear drive end is connected with actuating motor, a described left side, right hydraulic mechanism is connected with described driving gear and driven gear through the crank jointed gear unit, a described left side, the oil outlet of right hydraulic mechanism is connected a described left side respectively with actuator through one-way valve, the return opening of right hydraulic mechanism is connected with fuel tank through one-way valve respectively.
Further technological scheme, described hydraulic mechanism comprises an oil hydraulic cylinder, is provided with piston in the described oil hydraulic cylinder, described piston is inner to constitute hydraulic pressure cavity with the oil hydraulic cylinder inwall, is filled with hydraulic oil in it.
Further technological scheme, described piston outer end is hinged with connecting rod respectively in both sides up and down, and described connecting rod is hinged with driving gear and driven gear respectively, constitutes crank linkage driving system.
In the technique scheme, actuating motor links to each other with driving gear, the piston of hydraulic mechanism is connected with crank on driving gear and the driven gear via connecting rod as slide block, actuating motor according to the program start of compiling and edit after, the driving driving gear rotates, the rotation of driving gear driven gear symmetrical reverse promotes piston by connecting rod and does reciprocating linear motion.When driving gear rotated counterclockwise, the piston of left and right hydraulic mechanism is straight line motion left, and the hydraulic pressure cavity of right hydraulic mechanism sucks hydraulic oil by one-way valve, and the hydraulic pressure cavity of left hydraulic mechanism discharges hydraulic oil by one-way valve and enters actuator; After driving gear turned over 90 °, left and right two pistons are straight line motion to the right, and the hydraulic pressure cavity of left hydraulic mechanism sucks hydraulic oil, and right hydraulic mechanism discharges hydraulic oil; After driving gear turned over 180 ° again, reciprocation cycle action successively stopped until actuating motor.
Working principle of the present invention: actuating motor is the programmed settings curve in advance, mathematical analysis according to crank driving mechanism, can set up delivery pressure, the relation of flow and angle, adjust the size of pressure angle, realize the numerical control stepless pressure regulation, pressure angle is bigger, exportable low pressure and mass flow hydraulic oil, pressure angle hour, exportable high-pressure low-flow hydraulic oil, the output flow of an independent left oil hydraulic pump or right oil hydraulic pump is that q=|v|A(A is the inner area of piston), preestablish curve by the programming of numerical control servo motor, adopt left oil hydraulic pump in parallel with right oil hydraulic pump, according to its flow of formula be q=|v1|A1+|v2|A2=(| v1|+|v2|) A, by the numerical control servo motor, can set the piston movement speed waveform of single oil hydraulic pump, the piston movement speed waveform of another oil hydraulic pump is coupled with it, make the movement velocity of piston in left oil hydraulic pump and the right oil hydraulic pump | v1|+|v2|=C, C is a constant, left so in theory oil hydraulic pump can be coupled into straight line with flow curve after right oil hydraulic pump is in parallel, thereby realizes constant current output.
Because the technique scheme utilization, the present invention compared with prior art has following advantage:
1. the present invention is by being arranged in parallel left and right oil hydraulic pump, be arranged with left and right hydraulic mechanism in the oil hydraulic pump, driving gear and driven gear crank drive are connected left and right hydraulic mechanism respectively with between the two, left and right hydraulic mechanism return opening is connected with actuator through one-way valve respectively, driving gear is by driven by servomotor, thereby the constant current that has realized the plunger pump output flow is exported;
2. the component that do not run up among the present invention, and symmetrical configuration make the whole friction of device and shake lessly, and noise pollution is also less;
3. the present invention can realize the numerical control stepless pressure regulation by adjusting the size of pressure angle;
4. the present invention is simple in structure, controls easy to usely, and is easy to realize, is fit to promote the use of.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention one;
Fig. 2 is a left oil hydraulic pump output flow curve in the embodiment of the invention one;
Fig. 3 is a right oil hydraulic pump output flow curve in the embodiment of the invention one;
Fig. 4 is an output flow curve after the left and right oil hydraulic pump parallel connection in the embodiment of the invention one;
Fig. 5 is a left oil hydraulic pump output flow curve in the embodiment of the invention two;
Fig. 6 is a right oil hydraulic pump output flow curve in the embodiment of the invention two;
Fig. 7 is an output flow curve after the left and right oil hydraulic pump parallel connection in the embodiment of the invention two.
Wherein: 1, left oil hydraulic pump; 2, right oil hydraulic pump; 3, driving gear; 4, driven gear; 5, one-way valve; 6, fuel tank; 7, oil hydraulic cylinder; 8, piston; 9, hydraulic pressure cavity; 10, hydraulic oil; 11, connecting rod.
Embodiment
Below in conjunction with drawings and Examples the present invention is further described:
Embodiment one: referring to shown in Figure 1, a kind of double-action plunger pump, comprise left oil hydraulic pump 1 and right oil hydraulic pump 2, described oil hydraulic pump comprises a symmetrically arranged left side, right hydraulic mechanism, a described left side, be provided with a driving gear 3 between right hydraulic mechanism, be engaged with driven gear 4 with described driving gear 3, described driving gear 3 drive ends are connected with actuating motor, a described left side, right hydraulic mechanism is connected with described driving gear 3 and driven gear 4 through the crank driving mechanism, a described left side, the oil outlet of right hydraulic mechanism is connected with actuator through one-way valve 5 respectively, a described left side, the return opening of right hydraulic mechanism is connected with fuel tank 6 through one-way valve 5 respectively, described hydraulic mechanism comprises an oil hydraulic cylinder 7, be provided with piston 8 in the described oil hydraulic cylinder 7, described piston 8 inner and oil hydraulic cylinder 7 inwalls formation hydraulic pressure cavity 9 are filled with hydraulic oil 10 in it, described piston 8 outer ends are hinged with connecting rod 11 respectively in both sides up and down, described connecting rod 11 is hinged with driving gear 3 and driven gear 4 respectively, constitutes crank linkage driving system.
This device in use, each single oil hydraulic pump is controlled by the curvilinear motion of compiling and edit in advance through driving gear by actuating motor, the flow of latter two independent oil hydraulic pump output in parallel is a constant, adopt and wait the velocity curve that quickens-wait the deceleration triangular waveform, the single oil hydraulic pump of this waveform speed curve, its output flow is q=|v|A, referring to Fig. 2 and shown in Figure 3, left side oil hydraulic pump is in parallel with right oil hydraulic pump, its flow be q=|v1|A1+|v2|A2=(| v1|+|v2|) A, by the numerical control servo motor, making the movement velocity of piston in left oil hydraulic pump and the right oil hydraulic pump | v1|+|v2|=C, C are constant, and so left oil hydraulic pump can be coupled into straight line with flow curve after right oil hydraulic pump is in parallel, thereby realize constant current output, participate in shown in Figure 4.
Embodiment two: structure is identical with embodiment one.
This device in use, acceleration such as employing-at the uniform velocity-wait deceleration trapezoidal waveform velocity curve, the flow curve of independent left oil hydraulic pump or right oil hydraulic pump such as Fig. 5 and shown in Figure 6, the flow curve after two parallels connection of pumps as shown in Figure 7, thereby realize constant current output.
Claims (3)
1. double-action plunger pump, comprise left oil hydraulic pump (1) and right oil hydraulic pump (2), it is characterized in that: described oil hydraulic pump comprises a symmetrically arranged left side, right hydraulic mechanism, a described left side, be provided with a driving gear (3) between right hydraulic mechanism, be engaged with driven gear (4) with described driving gear (3), described driving gear (3) drive end is connected with actuating motor, a described left side, right hydraulic mechanism is connected with described driving gear (3) and driven gear (4) through the crank jointed gear unit, a described left side, the oil outlet of right hydraulic mechanism is connected a described left side respectively with actuator through one-way valve (5), the return opening of right hydraulic mechanism is connected with fuel tank (6) through one-way valve (5) respectively.
2. a kind of double-action plunger pump according to claim 1, it is characterized in that: described hydraulic mechanism comprises an oil hydraulic cylinder (7), be provided with piston (8) in the described oil hydraulic cylinder (7), described piston (8) is inner to constitute hydraulic pressure cavity (9) with oil hydraulic cylinder (7) inwall, is filled with hydraulic oil (10) in it.
3. a kind of double-action plunger pump according to claim 2, it is characterized in that: described piston (8) outer end is hinged with connecting rod (11) respectively in both sides up and down, described connecting rod (11) is hinged with driving gear (3) and driven gear (4) respectively, constitutes crank linkage driving system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110185308 CN102207066B (en) | 2011-07-04 | 2011-07-04 | Double-acting plunger pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110185308 CN102207066B (en) | 2011-07-04 | 2011-07-04 | Double-acting plunger pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102207066A true CN102207066A (en) | 2011-10-05 |
| CN102207066B CN102207066B (en) | 2013-02-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110185308 Expired - Fee Related CN102207066B (en) | 2011-07-04 | 2011-07-04 | Double-acting plunger pump |
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| CN (1) | CN102207066B (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103994044A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Crank connecting rod transmission type hydraulic pump with linear motor |
| CN103991780A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Plunger piston type hydraulic pump with double-output-shaft motor |
| CN103994045A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Plunger piston type hydraulic pump with linear motors |
| CN103994042A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Piston type hydraulic pump with crank connecting rod structure |
| CN104005925A (en) * | 2014-05-14 | 2014-08-27 | 苏州农业职业技术学院 | Plunger type hydraulic pump of transmission structure |
| CN105172513A (en) * | 2014-06-11 | 2015-12-23 | 株式会社万都 | Active suspension apparatus for vehicle and pump applied thereto |
| CN106337801A (en) * | 2015-07-08 | 2017-01-18 | 株式会社万都 | A method of setting zero point of bi-directional linear pump for active suspension apparatus |
| CN112814884A (en) * | 2021-01-13 | 2021-05-18 | 西南石油大学 | Flow pulsation reduction method under working condition of parallel conveying of double diaphragm pumps |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1401895A (en) * | 2002-09-13 | 2003-03-12 | 甘肃工业大学 | Double-acting four-plunger hydraulic delivery pump |
| US6705840B1 (en) * | 2002-06-19 | 2004-03-16 | Hydro-Gear Limited Partnership | Inline tandem pump |
| US6953327B1 (en) * | 2003-03-11 | 2005-10-11 | Hydro-Gear Limited Partnership | Dual pump |
| CN202117872U (en) * | 2011-07-04 | 2012-01-18 | 苏州大学 | Difunctional plunger pump |
-
2011
- 2011-07-04 CN CN 201110185308 patent/CN102207066B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6705840B1 (en) * | 2002-06-19 | 2004-03-16 | Hydro-Gear Limited Partnership | Inline tandem pump |
| CN1401895A (en) * | 2002-09-13 | 2003-03-12 | 甘肃工业大学 | Double-acting four-plunger hydraulic delivery pump |
| US6953327B1 (en) * | 2003-03-11 | 2005-10-11 | Hydro-Gear Limited Partnership | Dual pump |
| CN202117872U (en) * | 2011-07-04 | 2012-01-18 | 苏州大学 | Difunctional plunger pump |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103994044A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Crank connecting rod transmission type hydraulic pump with linear motor |
| CN103991780A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Plunger piston type hydraulic pump with double-output-shaft motor |
| CN103994045A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Plunger piston type hydraulic pump with linear motors |
| CN103994042A (en) * | 2014-05-14 | 2014-08-20 | 苏州农业职业技术学院 | Piston type hydraulic pump with crank connecting rod structure |
| CN104005925A (en) * | 2014-05-14 | 2014-08-27 | 苏州农业职业技术学院 | Plunger type hydraulic pump of transmission structure |
| CN104005925B (en) * | 2014-05-14 | 2016-08-24 | 苏州农业职业技术学院 | Use the pluger type hydraulic pump of drive mechanism |
| CN103991780B (en) * | 2014-05-14 | 2017-01-11 | 苏州农业职业技术学院 | Plunger piston type hydraulic pump with double-output-shaft motor |
| CN105172513A (en) * | 2014-06-11 | 2015-12-23 | 株式会社万都 | Active suspension apparatus for vehicle and pump applied thereto |
| CN106337801A (en) * | 2015-07-08 | 2017-01-18 | 株式会社万都 | A method of setting zero point of bi-directional linear pump for active suspension apparatus |
| CN112814884A (en) * | 2021-01-13 | 2021-05-18 | 西南石油大学 | Flow pulsation reduction method under working condition of parallel conveying of double diaphragm pumps |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102207066B (en) | 2013-02-27 |
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Address after: Suzhou City, Jiangsu province 215137 Xiangcheng District Ji Road No. 8 Patentee after: Soochow University Address before: 215123 Suzhou City, Suzhou Province Industrial Park, No. love road, No. 199 Patentee before: Soochow University |
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Granted publication date: 20130227 Termination date: 20150704 |
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