CN105526163A - Rapid oil applying method for high pressure vane pump - Google Patents
Rapid oil applying method for high pressure vane pump Download PDFInfo
- Publication number
- CN105526163A CN105526163A CN201510990203.4A CN201510990203A CN105526163A CN 105526163 A CN105526163 A CN 105526163A CN 201510990203 A CN201510990203 A CN 201510990203A CN 105526163 A CN105526163 A CN 105526163A
- Authority
- CN
- China
- Prior art keywords
- oil
- disturbance
- pump
- rotor
- vanes
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0088—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3445—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
The invention belongs to the hydraulic transmission technology, and particularly relates to a vane pump. After a single-vane type dual-action high-pressure vane pump is halted for a longer time, the oil temperature falls, and the viscosity rises; and when the oil pump is restarted, vanes are adhered to the interior of a rotor groove, in a low-temperature environment, oil applying is more difficult, and even oil is not applied to some pump fundamentally. The vane pump is characterized in that interfaces of the two ends of a rotor are each provided with a disturbance ring simple in structure, and the disturbance rings are fixed to a left oil distribution disc and a right oil distribution disc; and when the rotor drives the vanes to rotate, the vanes are collided to the outer side through the disturbance rings, then the vanes are pushed to the inner side through a curve face of a stator, the reciprocated motion is done two times each turn, the process is repeatedly executed, the vanes can be thrown out within an extremely-short time, and rapid oil applying is achieved. In addition, through application of the vane pump, the performance of the oil pump is improved, the service life of the oil pump is prolonged, and noise is remarkably reduced.
Description
Technical field
The invention belongs to hydraulic transmission technology, particularly a kind of single blade type high pressure vane pump.
Background technique
After single blade type high-pressure service pump stops for a long time, oil liquid temperature reduces, viscosity raises, and blade is bonded in rotor, restarts, and oil difficulty, if meet low temperature environment or use new pump, more obvious.Since first domestic PV series high voltage low-noise paddle pump comes out, because it is rational in infrastructure, stable performance, complete in specifications, working service convenient, noise is lower and by market extensive use.But this pump belongs to single leaf structure, on rear side of blade, gross area is subject to high pressure oil effect and presses to stator curved surface, produces larger friction and wear, directly affect performance and life-span in oil suction district.In order to control the impacting force of blade to stator, only having and reducing vane thickness as far as possible.Light due to blade relative thin, start under low temperature cold oil condition, because oil viscosity is high, blade centrifugal force is little, can not throw away formation enclosed space in time, is not easy to oil, and starting performance is poor, makes troubles to use.
For solving the difficult problem that oils, there is kind of a method to be adopt master cam to push stator curved surface to by rigid for each blade, forcing pump start work.Specific practice is: by a certain size of being a bit larger tham width of blade, does to bias internal by the actual stator curve used, and forms a little profiling elliptic curve, makes master cam accordingly, be arranged on inside left and right two food trays.When transmission shaft 9 rotates, little cam pushes blade to stator face successively, and pump starts to oil, and completes startup.But the method for the little cam of this employing profiling, for producing in serial form, quite bother, in a subfamily (or being pump group) product, have 7,8 specifications at least, there are 14,15 specifications at most, all will do corresponding little cam according to stator curve, quantity is many, and formality is tired of, and processing request is high, difficulty is large, less economical, is difficult to apply.
Summary of the invention
Under normal circumstances, the hydraulic oil viscosity for high-pressure service pump is inherently higher, and blade is thin and light, and under cold oil low-temperature condition, after pump start, it is constant that blade to be bonded in groove the radial position with rotor turns.Through reasonable time idle running after, along with rotor heat up oil viscosity is declined, blade gets rid of successively to stator curved surface under centrifugal action, finally completes and oils; Different product, different environment, complete the time difference oiled; And have some products, under low temperature cold deep-fried twisted dough sticks part, the idle running time extends also of no avail again.In order to improve this situation, the most direct way is increased in the gap of blade in groove, although the situation of oiling makes moderate progress like this, overall performance declines, and noise obviously rises, and is not the way of dealing with problems.
Solution of the present invention is: be bonded to actual conditions motionless in rotor for blade during oil pump cold start-up, we adopt perturbation method, disturbance ring is settled at two ends of rotor interface, rigid to oil suction district blade " to be hit " once, blade is forced outwards to move a certain distance, and forwarding laminated oil zone to, stator curved surface pushes back blade again inwards; Blade is forced to to-and-fro motion in rotor radial groove, and each transfers multiple 2 times to.If according to 1500 rpms of calculating, each blade each second of radial to-and-fro motion 50 times in rotor, so several seconds, in Shi Jimiao, the at most tens second time, because blade is by rapid perturbations heating, intensification, separate fluid around " having frozen " and get rid of to stator curved surface, oil pump completes very soon and oils, and proceeds to normal work, disturbance ring and blade again " to hit " less than.So from theory, how many different displacements specifications are comprised regardless of in certain subfamily (pump group), no matter namely there is the stator curve of how many different lifts (stator semi major axis R-stator short radius r), the problem as long as the startup having a kind of disturbance device just can solve whole subfamily product oils.
Accompanying drawing explanation
Fig. 1: the disturbance ring schematic diagram that apparatus of the present invention adopt.
Fig. 2: the concrete scheme of installation of disturbance ring during enforcement apparatus of the present invention.
Mark in figure: the diameter of bore φ of disturbance ring in Fig. 1
1, the radius of both sides eccentric arc is R
1, the overall width of ring is b
1, long to outside diameter circle be φ
2, two fixed hole diameters are φ
3, pitch-row is b2; Mark 1 in Fig. 2 and be depicted as disturbance ring, 2 is screws disturbance ring 1 is fixed on right food tray (not shown in FIG.), and 3 are depicted as rotor, 4 oil sucting cavities being depicted as left food tray, 5 is the pumping cavity of left food tray, 6 are depicted as stator, and 7 is stator negative camber, and 8 is oil guiding holes of stator, 9 is transmission shafts, 10 is straight pin, and 11 is pump core assembling screws, V
1, V
2, V
3for being in the blade in oil suction district respectively, φ
1and φ
4be respectively internal diameter and the external diameter of oil groove.
Embodiment
First the making of disturbance ring is considered.As mentioned above, in sub-series product, no matter include the stator curve of how many different lifts, as long as there is one (size) disturbance device in theory, just can solve the problem that oils of the numerous specification product of whole subfamily; Certainly, the product that the size of this device disturbance ring must meet minimum lift uses, and that is, blade is minimum one by the amplitude of disturbance (namely reciprocal distance) in rotor.Tell us according to general knowledge by practice: under identical forcing frequency, suitably increase perturbation amplitude, effect can be more obvious, and upper speed oil can be faster.For this reason during suggestion design disturbance ring, in the numerous lift of whole subfamily, select the stator parameter of a middle small dimension as the foundation determining fundamental mode disturbance ring, the most of specification product being more than or equal to this lift all can with this fundamental mode disturbance ring; To the part small dimension product being less than this lift, as long as the periphery of fundamental mode disturbance ring is slightly revised, mainly by its outside diameter circle φ
2reduce a little to meet use.
Suppose a selected middle small dimension stator, semi major axis is R, and short radius is r, so, and the width b of disturbance ring
1=2r-width of blade × 2-appropriate gap; The outside diameter circle φ of ring
2=2R-width of blade × 2-appropriate gap.As for endoporus φ
1, circular arc R 1, pitch-row b
2, aperture φ
3and the thickness of ring, can take the circumstances into consideration to determine according to structure.Perhaps the profile adopting multiple line segment to be linked to be is R close to radius
1camber line time, also can reach close effect, but the difficulty of processing of the working stability of pump and disturbance ring, be that the circular arc of same Radius is more excellent certainly.
Implement this method and also need respectively process an annular oil groove in the both ends of the surface of the inner side surface of left and right oil distribution casing, rotor, the dimension of inner and outer diameters of groove is shown in φ in Fig. 2
1and φ
4shown in, the degree of depth sum of two grooves should guarantee to hold disturbance ring in opposite directions, and leaves axis and radial gap, and the annular groove degree of depth wherein inside two oil distribution casings is got about 40% of disturbance ring thickness and is advisable, all the other size constancies.
Finally should turn to according to oil pump before assembling, namely press stator major diameter direction, two disturbance rings are arranged in the annular groove of left and right oil distribution casing respectively, and fix with two nails, all the other conveniently assemble.Turning to change oil pump, only disturbance ring half-twist need be installed.If blade rear end face can be done small angle chamfering or the process of rounding arc, then effect is better.With the vane pump of apparatus of the present invention, thoroughly can not only solve the difficult problem that oils, and the matching gap of moderate compression vane thickness, minimizing blade and rotor becomes possibility, and whole pump performance, stability and life-span are increased, and noise is even more ideal.
Claims (4)
1. its device of the method that oils fast of a high pressure vane pump is respectively made up of the left food tray of an annular oil groove and right food tray the rotor 3 of an annular oil groove and inner side surface respectively primarily of disturbance ring 1, screw 2, two ends, and this outer leafs is (as V
1) be contained in rotor, the inner chamber that rotor 3 is placed in stator 6 is driven by transmission shaft 9, the two ends of stator 6 are left and right food tray, by two pieces of straight pins 10, three is connected, and be assembled into a pump core assembly with two pieces of assembling screws 11, it is characterized in that two disturbance rings 1 are placed in the annular groove at two ends of rotor and food tray interface respectively, said screw 2 is separately fixed at two disturbance rings 1 on left and right food tray according to stator major diameter direction.
2. preparation device fast as claimed in claim 1, the periphery that it is characterized in that disturbance ring 1 is R by two sections of radiuses respectively
1eccentric arc and two sections of diameters be φ
2circular arc formed, and diameter of bore φ
1, two hole diameters are φ
3, holes pitch-row b
2and the thickness of disturbance ring 1, can take the circumstances into consideration to determine according to structure.
3. preparation device fast as claimed in claim 1, what it is characterized in that determining according to subfamily whole structure has outside diameter circle φ
2fundamental mode disturbance ring 1, when lift product little of part, only need micro-ly to repair periphery, mainly by outside diameter circle φ
2repair a little and littlely can meet usage requirement.
4. preparation device fast as claimed in claim 1, is characterized in that the radial dimension of processed food tray interior annular oil groove is identical with rotor end-face annular groove; Axial depth is got about 40% of disturbance ring 1 thickness and is advisable.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510990203.4A CN105526163A (en) | 2015-12-21 | 2015-12-28 | Rapid oil applying method for high pressure vane pump |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510961650 | 2015-12-21 | ||
| CN2015109616507 | 2015-12-21 | ||
| CN201510990203.4A CN105526163A (en) | 2015-12-21 | 2015-12-28 | Rapid oil applying method for high pressure vane pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105526163A true CN105526163A (en) | 2016-04-27 |
Family
ID=55768593
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510990203.4A Pending CN105526163A (en) | 2015-12-21 | 2015-12-28 | Rapid oil applying method for high pressure vane pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105526163A (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08219046A (en) * | 1995-02-16 | 1996-08-27 | Nakamura Kimie | Oil-free vane type fluid machine |
| CN2438849Y (en) * | 2000-09-07 | 2001-07-11 | 成都海普特电子机械技术开发有限责任公司 | Low-rotating speed vane pump |
| US20030044300A1 (en) * | 2001-08-30 | 2003-03-06 | Akira Osugi | Vane pump |
| CN2572048Y (en) * | 2002-09-13 | 2003-09-10 | 赵来福 | Efficient rotor type thickened oil pump |
| CN103321896A (en) * | 2012-03-22 | 2013-09-25 | 日立汽车系统株式会社 | Vane pump |
| CN103321901A (en) * | 2013-07-05 | 2013-09-25 | 王洪继 | Vane pump |
| CN203335393U (en) * | 2013-07-05 | 2013-12-11 | 王洪继 | Vane pump |
| CN203867886U (en) * | 2014-05-07 | 2014-10-08 | 胡凯 | Improved hydraulic pump |
| CN205533196U (en) * | 2015-12-21 | 2016-08-31 | 吴一佳 | Device that oils fast of high pressure vane pump |
-
2015
- 2015-12-28 CN CN201510990203.4A patent/CN105526163A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08219046A (en) * | 1995-02-16 | 1996-08-27 | Nakamura Kimie | Oil-free vane type fluid machine |
| CN2438849Y (en) * | 2000-09-07 | 2001-07-11 | 成都海普特电子机械技术开发有限责任公司 | Low-rotating speed vane pump |
| US20030044300A1 (en) * | 2001-08-30 | 2003-03-06 | Akira Osugi | Vane pump |
| CN2572048Y (en) * | 2002-09-13 | 2003-09-10 | 赵来福 | Efficient rotor type thickened oil pump |
| CN103321896A (en) * | 2012-03-22 | 2013-09-25 | 日立汽车系统株式会社 | Vane pump |
| CN103321901A (en) * | 2013-07-05 | 2013-09-25 | 王洪继 | Vane pump |
| CN203335393U (en) * | 2013-07-05 | 2013-12-11 | 王洪继 | Vane pump |
| CN203867886U (en) * | 2014-05-07 | 2014-10-08 | 胡凯 | Improved hydraulic pump |
| CN205533196U (en) * | 2015-12-21 | 2016-08-31 | 吴一佳 | Device that oils fast of high pressure vane pump |
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|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20160427 |