CN101922425B - Axial plunger pump for increasing flow and sealing pressure - Google Patents
Axial plunger pump for increasing flow and sealing pressure Download PDFInfo
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- CN101922425B CN101922425B CN200910052712A CN200910052712A CN101922425B CN 101922425 B CN101922425 B CN 101922425B CN 200910052712 A CN200910052712 A CN 200910052712A CN 200910052712 A CN200910052712 A CN 200910052712A CN 101922425 B CN101922425 B CN 101922425B
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- swash plate
- pressure
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Abstract
The invention relates to an axial plunger pump for increasing flow and sealing pressure, belonging to the hydraulic pressure industry of general machinery field. Compared with the traditional pump which has one set of booster system, the axial plunger pump has two sets of booster system, wherein the highest points of two inclined discs ( part 1 and part 2 shown in the chart) differ 180 DEG so that the two sets of plungers (part 4 and part 5 shown in the chart) boost in pair to balance moment acting on a valve plate (part 8 shown in the chart) to uniform the sealing pressure in the front and at the back of the valve plate so as to seal higher pressure; a cylinder sleeve (part 6 shown in the chart) made of Si3N4 is added in the fit clearance of the plungers and a cylinder body (part 7 shown in the chart) to improve clearance sealing and cylinder body strength; and by the measures of the invention, the maximum flow and the pressure of the pump are greatly increased. High-pressure and large-flow pumps are used for large-sized oil-pressure or hydraulic-pressure machinery to greatly reduce the volume of main engine thereof, and thus, the manufacture difficulty is reduced, the volume and the quantity of the matched axial plunger pump is reduced, a large-sized oil press can be manufactured, and project cost and construction cost are greatly saved.
Description
Technical field
The invention belongs to the pump class industry in the fluid machinery in the universal machine field.Pump often is called as the heart of machine.Its delivery hydraulic pressure has a machine in operation.Axial piston pump is higher a kind of of pressure in the pump class.It is widely used in the field such as operation system, automatic control system and metallurgy, petrochemical industry of oil hydraulic press, universal machine, machine.
Background technique
The world-technology progress, some field is developed from large-scale direction, big gun, aircraft, steamer, high building or the like.Make airplane carrier, be unable to do without oversized ten thousand tons of oil hydraulic presses.Oversized ten thousand tons of oil hydraulic presses need the pump of high-pressure high-flow supporting.Only there is few countries can produce oversized equipment as airplane carrier at present in the world.They have the technology of its oneself high-pressure high-flow pump.China is badly in need of catching up with and surpassing.The pressure of China's axial piston pump unit is commonly used at present only reaches 32Mpa, and flow is no more than 500 liters/Min, with advanced country high pressure 60Mpa bigger gap is arranged.Can not satisfy super-huge equipment far away and be badly in need of the requirement of development, can only lean on import.The present invention both provided the supporting needs of the super-huge machinery development of present China, had filled up national blank, also did one's bit for development China advanced manufacturing industry.
Summary of the invention
Existing axial piston pump only has a cover booster system, and its key structure is made up of four parts, shown in Figure 1 as in the Figure of description: the swash plate 1 with 15 °～20 ° of inclination angles.7 plungers 2 that are distributed on the circle (being called distribution circle) are arranged on the swash plate.The cylinder body 3 that 7 vestibules (corresponding with the distribution circle of plunger and supply 7 plungers come and go to slide) are arranged.The thrust plate 4 that one circle flow path groove is arranged.There are not special material and special construction.
If will improve the working pressure of pump; This class formation has fatal shortcoming; Turnover oil (broadly claiming medium) passage of pump all passes the interface of thrust plate and cylinder body, thrust plate and the pump housing; And the oil-feed of confession and two fuel-displaced semi-circular flow grooves are arranged between the interface of the thrust plate and the pump housing, the plane sealing structure that this a series of sealing all adopts simple two planes to compress mutually, and each interplanar pressure leans on first loop pillar plug of distribution circle (3～4) boosting when advancing to produce entirely.And meanwhile, also have other half-turn plunger (4～3) retreating on the distribution circle and vacuumize, carry out oil suction (seeing Fig. 1 sectional drawing).Therefore, the force-bearing situation on the thrust plate sealing surface is that half compresses half and pulls open all the time, shown in Fig. 2 sectional drawing.Pulled open the interference of active force, the sealing force of pressing section is just very inhomogeneous.This just exists the trend of the flow direction normal pressure flow groove of high pressure flow groove, thereby has limited the raising of this type of pump work pressure.
The invention of the axial piston pump of this augmented flow and sealing load mainly contains three broad aspect.
At first, in a pump, increase by a cover booster system, become a pump two cover booster systems (Fig. 3): 1. two swash plates, one of them is called interior swash plate (part 1 among Fig. 3) and outer swash plate (part 2 among Fig. 3) respectively in another outer ring.The gradient on two swash plate inclined-planes is respectively 13 °～15 °, 10 °～13 °, and the peak on two swash plate inclined-planes (on the long axis of ellipse of border, inclined-plane) is not at homonymy, but (abbreviation phase angle) the 180 ° of angles of staggering each other.2. on two swash plates, respectively dispose one group of plunger (for example 7 every group, part 4 and part 5 among totally 14-Fig. 3), they are distributed in respectively on the distribution circle separately.3. the vestibule (A-A sectional drawing among Fig. 3) that design two circles and plunger are complementary in a cylinder body (part 7 among Fig. 3).4. design a thrust plate (plan view among Fig. 4) that inside and outside two circle flow path grooves are arranged.More than the effect of invention at first is that two cover booster systems increase pump duty greatly; Secondly, see pump one running from operating principle; When arbitrary plunger advancement of inner ring boosted; The place, 180 ° of angles that is separated by, the position of plunger must have a plunger to advance simultaneously to boost therewith in the outer ring, makes thrust plate receive the effect (Fig. 4 midship section figure) of centrosymmetric two equal moments all the time, in like manner; When being in together, the whole half-turn plunger of inner ring advances when boosting; The plunger that outer ring, opposite phase angle locates to have equal number for 180 ° also boosts advancing, and produces identical moment with inner ring plunger pressure, and consequently right (S) (Fig. 4 sectional drawing) sealing load in the left side (L) of (about being depicted as among the figure) two sealing surfaces is balanced everywhere all the time before and after the thrust plate equates; This sealing configuration just can be sealed higher pressure, has solved the sealing problem of pumping pressure raising back flow groove and passage thereof.
Secondly, supply all plungers to come and go in each hole of sliding at cylinder body, respectively adorn a jacket casing (part 6 among Fig. 3) with the hole interference fit, the jacket casing material is Si
3N
4Or ZrO
2This innovation has solved three big problems: 1. because the cylinder body prestressed structure can reduce its stress level, improve the ability of bearing pressure, this has just solved the strength problem of working pressure raising rear-bank rotor housing; 2. plunger rapid movement back and forth in jacket casing, the gap between plunger and the jacket casing is that dielectric leakage must be through part (being called clearance seal).The gap, little can killing because of plunger rapid movement frictional heating expands, big can be because of from the gap, too much the run off required pressure of lose normal flow rate even formation not of medium.Fluid mechanics proves that fluid is directly proportional with the biquadratic in pressure, gap through the flow of annular space, is inversely proportional to the viscosity of fluid, the length in gap.Particularly, intrinsic primary clearance increases along with the raising of pressure, and the flow of leakage is strengthened rapidly, causes clearance seal to lose efficacy, and this also is the insoluble problem of existing pump.This prestressed structure jacket casing material can slow down the gap with the effect that the raising of pressure increases, and has also just stoped the increasing rapidly of the flow that leaks, and has solved the sealing problem here after pumping pressure improves.3. mesohigh high-velocity fluid in gap is very severe to the erosive wear of casing wall, and the jacket casing material that the present invention selects for use belongs to high abrasion damage type, after having solved pumping pressure and improving, and problem sealing life here.
The 3rd, on the inclined-plane of two swash plates, wear washer (part 3 among Fig. 3) is housed respectively.After pumping pressure improved, specific pressure suffered on the swash plate inclined-plane increased thereupon, and the frictional force that is directly proportional with specific pressure also increases; Add the effect of the impulse force of ramp angle of climb running; The operating mode on swash plate inclined-plane is more abominable, if cooling and antifriction are improper, will ablate; On this inclined-plane, installed wear washer additional, solved the ablation problem here when pump turns round under elevated pressures.
Description of drawings
Fig. 1 shows that existing axial piston pump only has the key structure of a cover booster system, and plan view the right is a swash plate 1, and its left surface is the inclined-plane; Top is minimum point, and the bottom is a peak, and figure is last to be shown; When cylinder body 3 rotations, it will be with plunger 2 to rotate together, suppose that the direction of rotation is the direction of arrow along the A-A sectional drawing left side; The plunger that then is positioned at left side L advances toward a high position along the swash plate inclined-plane from low level and boosts, and under the effect of the reaction force of its hole medium pressure and central spring power (omitting among the figure), the right-hand member of all plungers is close to (across piston shoes) swash plate inclined-plane all the time and does not leave; This just shows; When the plunger of left side L when boosting, the plunger of the right R is retreated toward low level from high-order along the swash plate inclined-plane, plays a part to vacuumize oil suction.Plunger front end vestibule cause the extremely uneven propagation of pressure of two demifacets of cylinder body to thrust plate 4 about face, provide the sealing load at interface to seal.Being positioned at the thrust plate left side is the pump housing 5, and it plays a part the oily passage of turnover.
The stressing conditions of the sealing surface of thrust plate 4 when Fig. 2 is the pump running: press the sense of rotation shown in the figure one; The first quarter moon alveolus of plan view left side demifacet is to meet and send off the high-pressure trough that the plunger that boosts is sent high pressure oil here, and the first quarter moon alveolus of right-half plane is the trough of low pressure that connects the lifting plunger oil suction.Lower plane on the following sectional drawing (agreement) is represented the interfacial plane of thrust plate and cylinder body, thrust plate and the pump housing respectively.The direction of arrow on the plane representes that thrust plate receives force direction, and long big arrow points sealing surface representes that left demifacet effect big sealing load, and short little arrow points deviates from sealing surface and representes that right-half plane has the active force of less counteracting sealing load.Pump is in when operation, and cylinder body rotation, plunger not only rotate but also seesaw, swash plate and thrust plate are fixed, explains that the big or small inequality of sealing load at thrust plate interface exists all the time.
Fig. 3 shows the main structure of pump of the present invention: interior swash plate 1, outer swash plate 2 on its outside, its inclined-plane, be equipped with respectively on wear washer 3, interior swash plate and the outer swash plate respectively to 7 plungers 5 of 7 plungers 4 of inner ring and outer ring should be arranged, they are contained in the jacket casing 6 of respective numbers respectively, jacket casing 6 merges with cylinder body 7 close-fittings respectively makes that plunger and cylinder body are separated, they rotate on the right side of thrust plate 8, the left side of thrust plate 8 is the pump housings that only supply the medium access way.Interior swash plate differs 180 ° with the peak that outer swash plate is mounted to its inclined-plane; When the cylinder body band two loop pillar plugs and is rotated together; If sense of rotation is shown in the arrow on the A-A sectional drawing left side among the figure; Then the plunger of the plunger of inner ring left side demifacet and outer ring right-half plane all slides to peak from the minimum point on swash plate inclined-plane separately, advances simultaneously and boosts.Equally, the plunger of the plunger of inner ring right-half plane and outer ring left side demifacet all moves back to minimum point step-down simultaneously from the peak on swash plate inclined-plane separately.Exist in pairs because the Internal and external cycle plunger is the central shaft about the relevant part of pump, the plunger of process is three, four or more than three, always there is the plunger of the same quantity in outer ring to boost together no matter inner ring boosts.The pressure that is produced is delivered on the thrust plate together.
Fig. 4 shows the stressing conditions of the sealing surface of the on-stream thrust plate 8 of pump: by sense of rotation shown in Figure 3; The first quarter moon alveolus of plan view left side demifacet inner ring and the first quarter moon alveolus of right-half plane outer ring all are to meet and send off inner ring and the outer ring plunger that boosts to send the passage high-pressure trough of high-pressure medium here; The distance at two high-pressure troughs and thrust plate center is respectively R1 and R2, and this also is that the Internal and external cycle plunger belongs to the distribution radius of a circle separately.The first quarter moon alveolus of the first quarter moon alveolus of right-half plane inner ring and left demifacet outer ring all is the trough of low pressure of lifting plunger oil suction (medium).The last lower plane (agreement) of sectional drawing is represented the interfacial plane of thrust plate and cylinder body, thrust plate and the pump housing respectively.Explanation like Fig. 3 is said, and the plunger of inner ring left side demifacet and the plunger advancement of outer ring right-half plane are boosted, and pressure passes on these interfacial plane, is expressed as F1 and F2 among the figure.F1 and F2 produce two moment M1 and M2 respectively:
M1＝R1×F1，
M2＝R2×F2
Fig. 5 shows the situation of equivalent force, the effect of strong F1 of the one side of thrust plate and F2, and the moment that lets them produce respectively equates:
M1＝M2
R1 * F1=R2 * F2 then,--------------------(1)
Power F1 and F2 come equivalence to the equilibrating force system shown in the available Fig. 5 a of the result of thrust plate effect or Fig. 5 b.Then the another side of thrust plate can with in the opposite direction a, size equal F1 and F2's and, point of action comes balance at synthetic total power F0 at thrust plate center:
F0＝F1+F2---------------------(2)
Fig. 6: synthetic total power F0 comes equivalence to the also available equilibrating force system shown in Figure 6 of the result of thrust plate effect.Then its central role of the one side of thrust plate total power F0, and another side can be in the opposite direction with two circles, point of action comes balance at sealing load g1 and the g2 of decentre R1 and R2.Through design, can make the size of sealing load (pressure) g1 and g2 be tending towards impartial, reach the purpose that sealing is not here leaked.
Embodiment
At first, in the manufacturing of pump of practical implementation two cover booster systems, solve three problems:
1. stagger 180 ° each other for swash plate in realizing and outer swash plate peak (on the long axis of ellipse of border, inclined-plane); Must rule in advance to workpiece; As the line of reference of inclined-plane highs and lows, this line of reference joins through the center of workpiece both ends of the surface and with the workpiece segment of a cylinder, marks the bus that this connects the inclined-plane highs and lows at the workpiece cylinder; Processing also keeps this bus line of reference all the time on the coordinate lathe; During assembling, interior swash plate and outer swash plate bus line of reference are aimed at, swash plate staggers 180 ° each other with outer swash plate peak in just guaranteeing.
2. in order to solve the backhaul dynamical problem of outer ring plunger, the front that can be employed in the outer ring plunger is installed pressure spring, also can be employed in the method solution that installation rolling bearing in inside pump casing or the interior swash plate outside blocks platen.
3. when the radius R 1 of specifically confirming two distribution gardens and R2, consider with the size of Internal and external cycle plunger diameter d1 and d2.Make them satisfy equalising torque formula (1)
R1×F1＝＝R2×F2---------------------(1)
Because: F1=0.25 π d1
2, F2=0.25 π d2
2,-----------(3)
(3) substitution (1)
Can get
R1×d1
2＝＝R2×d2
2
Or
R2＝R1×d1
2/d2
2--------------------(4)
During design,, by the radius R 2 of the definite outer distribution circle of formula (4).
Secondly, implement the interference fit of jacket casing and cylinder body, two measures are arranged: 1. the Mechanics Calculation of passing through the hybrid type theory of strength; Choose the size of magnitude of interference; The internal stress of adjustment cylinder body and jacket casing makes jacket casing and cylinder body all have enough safety coefficient, under high pressure is unlikely damage; For the outer diameter of jacket casing greater than each bore dia of corresponding cylinder body, the method for available hot jacket then expands its each hole, carries out the hot jacket assembling when each hole of treating cylinder body is expanded to greater than the outer diameter of jacket casing.
Claims (5)
1. an axial piston pump that increases flow and sealing load is characterized in that: designed two cover booster systems, wherein; One cover booster system contains interior swash plate, and another set of booster system contains outer swash plate, and outer swash plate is in the outer ring of interior swash plate; The Transverse plane of the Transverse plane of swash plate and outer swash plate coexists on the equidirectional plane in this, and another equidirectional Transverse plane of interior swash plate and outer swash plate all is the inclined-plane, and respectively there is the peak of oneself on two inclined-planes; Also be two swash plates peaks separately, the position of two peaks is relative each other, differs 180 ° of angles; Between plunger and cylinder body, design sealing sleeve, on the inclined-plane of two swash plates, designed wear washer respectively.
2. a kind of axial piston pump that increases flow and sealing load according to claim 1; It is characterized in that: the gradient on two swash plate inclined-planes is respectively 13 °～15 °, 10 °～13 °; The peak on two swash plate inclined-planes is not at homonymy, but the 180 ° of angles of staggering each other.
3. a kind of axial piston pump that increases flow and sealing load according to claim 1; It is characterized in that: designed the identical inner ring plunger of quantity and at the peripheral outer ring plunger of inner ring plunger; One circle inner ring vestibule is being arranged on the cylinder body and outside it, be with the circle outer ring vestibule identical with its quantity, thrust plate has two cover flow path grooves.
4. a kind of axial piston pump that increases flow and sealing load according to claim 1 is characterized in that: the used material of jacket casing is Si
3N
4Or ZrO
2, it and cylinder body adopt the drive fit structure.
5. a kind of axial piston pump that increases flow and sealing load according to claim 3 is characterized in that: through in the inside pump casing or the interior swash plate outside method that rolling bearing blocks platen being installed, solve the backhaul dynamical problem of outer ring plunger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910052712A CN101922425B (en) | 2009-06-09 | 2009-06-09 | Axial plunger pump for increasing flow and sealing pressure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910052712A CN101922425B (en) | 2009-06-09 | 2009-06-09 | Axial plunger pump for increasing flow and sealing pressure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101922425A CN101922425A (en) | 2010-12-22 |
| CN101922425B true CN101922425B (en) | 2012-10-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910052712A Expired - Fee Related CN101922425B (en) | 2009-06-09 | 2009-06-09 | Axial plunger pump for increasing flow and sealing pressure |
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| Country | Link |
|---|---|
| CN (1) | CN101922425B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103939312B (en) * | 2014-04-25 | 2016-07-06 | 福州大学 | A kind of double huge discharge axial plunger pump of balanced type |
| CN108302000A (en) * | 2017-12-30 | 2018-07-20 | 孟庆仕 | A kind of inclined disc type oscillating plunger pump of balanced radial force |
| CN112012899B (en) * | 2020-07-09 | 2021-10-22 | 浙江大学 | Quick reversing hydraulic driving device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2247728Y (en) * | 1995-06-01 | 1997-02-19 | 徐绳武 | Double swashplate two-way flow axial plunger pump |
| CN1233720A (en) * | 1999-05-18 | 1999-11-03 | 徐维胜 | Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit |
| CN2799306Y (en) * | 2005-05-31 | 2006-07-26 | 何俊凤 | Automobile energy reusing device |
| DE102006037593A1 (en) * | 2006-08-11 | 2008-02-14 | Robert Bosch Gmbh | Swash plate machine with rotating cylinders includes sound-deadening elastomer layers in control disc supported against end plate of machine casing |
-
2009
- 2009-06-09 CN CN200910052712A patent/CN101922425B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2247728Y (en) * | 1995-06-01 | 1997-02-19 | 徐绳武 | Double swashplate two-way flow axial plunger pump |
| CN1233720A (en) * | 1999-05-18 | 1999-11-03 | 徐维胜 | Double inclined plate synchronous rotation internal power split stream hydraulic variable speed unit |
| CN2799306Y (en) * | 2005-05-31 | 2006-07-26 | 何俊凤 | Automobile energy reusing device |
| DE102006037593A1 (en) * | 2006-08-11 | 2008-02-14 | Robert Bosch Gmbh | Swash plate machine with rotating cylinders includes sound-deadening elastomer layers in control disc supported against end plate of machine casing |
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| Publication number | Publication date |
|---|---|
| CN101922425A (en) | 2010-12-22 |
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Granted publication date: 20121017 Termination date: 20170609 |