CN1544814A - Medium-high pressure gear pump having asymmetric double-circular-arc gear shape - Google Patents
Medium-high pressure gear pump having asymmetric double-circular-arc gear shape Download PDFInfo
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- CN1544814A CN1544814A CNA2003101052062A CN200310105206A CN1544814A CN 1544814 A CN1544814 A CN 1544814A CN A2003101052062 A CNA2003101052062 A CN A2003101052062A CN 200310105206 A CN200310105206 A CN 200310105206A CN 1544814 A CN1544814 A CN 1544814A
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Abstract
The invention is a nonsymmetrical double-arc tooth form medium- and high- pressure gear pump, two gears on the driving shaft are staggered at half tooth form angle in circumferential direction, there is no baffle between the inside end face of the two gear pairs, there I a floating pressure side plate between outside end face and left-and-right end covers, and the gear top contacts and hermetically cooperates with the arc surface of the inner cavity in the pump case, where the driving shaft are connected with the two gears through keys, and the driven shaft is connected with a gear by key and the other is covered on the driven shaft, and the two engaging gear pairs can be helical cylindrical gears at equal helical angle and in opposite rotating direction. Its advantages: it can prolong the service life of gears, preventing oil leakage, implementing medium- and high- pressure transmission of the gear pump, the working pressure reaches above 6MPa and it reduces flow pulsating rate of the gear pump by 75% in comparison with involute gear pump, make the pump work more stably and the noise lower.
Description
Technical field the present invention relates to a kind of gear pump, the arc toothed mesohigh gear pump of specifically a kind of asymmetric double.
Background technique is in hydraulic transmission and control technique, gear pump occupies extremely important position, it is widely used in the hydraulic systems such as lathe, building, oil field, advantage such as the number of teeth is few, volume is little though circular-arc gear pump now has, no undercut, pulsating movement free, stable drive, noise are low, but can only under low pressure work, application area is extensive inadequately.
Summary of the invention the objective of the invention is to overcome deficiency in the prior art, and it is arc toothed to have proposed new asymmetric double, and designs the arc toothed mesohigh gear pump of a kind of asymmetric double.Except that keeping original circular-arc gear pump advantage, pressure is brought up to mesohigh, promptly belong to the engagement system of innovation.Because profile of tooth is asymmetric, so can be divided into active side and non-working side, usually the side that pressure angle is big is as active side, this side is because the big endurance life of pressure angle, contact strength, anti-spot corrosion intensity is all high, thereby can improve gear capacity and life-span, the side that pressure angle is little is a non-working side, original this side also can adopt and the same big pressure angle of active side, but tooth top can come to a point too early like this, because this side is not worked, can not influence pump performance so this side intensity is low slightly, the big I in pressure at both sides angle is chosen after optimal design, the profile of tooth active side is meshed with active side during engagement, the non-working side servo-actuated.
Asymmetric double circular arc two gears that are meshed all adopt same profile of tooth, and its profile of tooth is made up of two sections circular arcs, and tooth top partly is the dome arc, and tooth root partly is a concave circular arc.Therefore, asymmetric Double circular arc gear drive just is equivalent to the work that is combined with each other of two pairs of single-circular-arc gears.In the transmission process, a pair of is that double wedge drives recessed tooth work, and an instantaneous point of contact is arranged, and another is to being the moving double wedge work of recessed cingulum, point of contact of instantaneous generation.Therefore, in transmission process, before and after node, two line of contact are arranged simultaneously, and instantaneous two point of contact lay respectively in two different end faces.The Novikov gears with double circular arc tooth profiles of using aborning has the common tangent formula and divides stepwise two kinds of forms at present: the present invention adopts segment double circular arc gear, and protruding, recessed flank profil is carried out tangent modification, then forms the segment double circular arc gear basic rack tooth profile.Segment double circular arc gear connects protruding, recessed working flank with circular arc, so its transition portion is stepped form.Design philosophy in conjunction with the asymmetric double circular tooth gear, actual design a kind of asymmetric double circular arc mesohigh gear pump: two ends, the pump case left and right sides are provided with end cap, the tooth-shape angle that circumferentially staggers half of two gears on the driving shaft, be provided with dividing plate between the inner side end of two pairs of gears that are meshing with each other, be provided with the floating pressure side plate that is enclosed within on driving shaft and the driven shaft between the outside end face and the left and right sides end cap, sweep thorax by tooth top and constitute tooth top and contact the radial seal cooperation with pump case inner chamber arc surface.Two pairs of engaging gears, wherein 2 gears are by key connecting on the driving shaft, and 1 gear is by key connecting on the driven shaft, and another geared sleeve is on driven shaft.The helical gear that the two pairs of engaging gears are the helix angle equal and opposite in direction, rotation direction is opposite.
The present invention compared with prior art has following advantage: the arc toothed gear endurance life that improves of asymmetric double, anti-spot corrosion intensity, contact strength, and then can improve gear life, dividing plate between the two pairs of engaging gears prevents to scurry oil, circular tooth gear has carried out sweeping the thorax design, tooth top is that arc surface contacts with the pump case inner chamber, thereby changed the shortcoming of line contact, the floating pressure side plate lateral seal that cooperates two end part again, realized that the gear pump mesohigh transmits, promptly existing circular-arc gear pump rated working pressure is about 0.6Mpa, and working pressure of the present invention reaches more than the 6Mpa, because adopt circumferential zigzag tooth structure, the present invention compares with involute gear pump, the pumping flow pulsation rate has reduced by 75%, it is more steady to work, and noise is lower.
Description of drawings
Fig. 1 is a gear pump fundamental diagram of the present invention.
Fig. 2 is the asymmetric tooth profile of double circular-arc gears figure of the present invention.
Fig. 3 is a structural representation of the present invention.
Fig. 4 is the A-A sectional view of Fig. 3.
Now the invention will be further described in conjunction with the accompanying drawings for embodiment, with reference to Fig. 1, a pair of gear intermeshes, because the tooth top and the pump case internal surface gaps of gear are minimum, gear face and floating pressure side plate gap are also very little, thereby oil sucting cavity e and pumping cavity f are separated.When engaging gear rotates by direction as shown, the tooth that is meshing on the point of mesh right side withdraws from engagement gradually, the space increases, and forms parital vacuum, and the oil in the fuel tank enters oil sucting cavity under the external atmosphere pressure effect, the tooth in point of mesh left side progresses into engagement, the fluid of between cog is pushed out, force outflow, Here it is the oil suction of gear pump and the process of pressure oil from pumping cavity, when gear constantly rotated, gear pump is oil suction constantly and pressure oil just.
Fig. 2 has provided the asymmetric tooth profile of double circular-arc gears of gear pump of the present invention, and the technical specifications of this gear pump are:
(1) this pump design discharge capacity 68ml/r
(2) prime mover rated speed 1450r/min prime mover maximum speed 1800r/min
(3) working pressure (specified) 6.3Mpa Maximum operating pressure 10Mpa (4) efficient 90%
Discharge capacity of the present invention determines according to the pump standard, after discharge capacity of the present invention is determined, just can draw parameter z, m, the b etc. of this asymmetric double circular tooth gear, as normal module m
n=5 tooth number Z=12 o'clock then can obtain following asymmetric double circular tooth gear tooth profile parameter:
Active side pressure angle α
1=24 °
Non-working side pressure angle α
2=15 °
Whole depth h
Addendum ha
Dedendum of the tooth hf
Double wedge flank profil radius of arc ρ a
Recessed tooth flank profil radius of arc ρ f
The chordal thickness sa of double wedge point of contact place
The chordal thickness sf of place, recessed toe joint contact
The groove width ef of place, recessed toe joint contact
Double wedge flank profil center of circle side-play amount la
Recessed tooth flank profil center of circle side-play amount lf
The double wedge flank profil center of circle is moved apart from amount xa
The recessed tooth flank profil center of circle is moved apart from amount xf
Double wedge process corner δ=6 20 52 "
Recessed tooth process corner δ=9 19 30 "
Point of contact is to the distance h k of nodel line
Connect the distance h ja of the point of contact of circular arc and double wedge circular arc to nodel line
Connect the distance h jf of the intersection point of circular arc and recessed tooth circular arc to nodel line
The tooth waist connects radius of arc rj
Fillet radius rg
Fig. 2 shows that asymmetric tooth profile of double circular-arc gears is made up of two sections circular arcs, and tooth top partly is the dome arc, and tooth root partly is a concave circular arc, and connects the convex-concave working flank with circular arc, and its transition portion is stepped form.
Fig. 3 is the structural representation of gear pump of the present invention, and this asymmetric double circular tooth gear parameter is as follows: normal module m
n=5 tooth number Z=12 helixangles=8 ° active side pressure angle α
1=24 ° of three pieces type structures that the pump housing is made up of left end cap 1, line pump housing 3, right end cap 9.It is easy to manufacture that the three pieces type structure has blank, easy to use, is convenient to machining, is convenient to arrange advantages such as bidirectional hydraulic compensation.Be provided with the dividing plate 7 that prevents to scurry oil between the inner side end of two pairs of engaging gears, outside end face is by being provided with floating pressure side plate 4,11 between pad 5,13 and the left and right sides end cap, two gears 6,8 on the driving shaft 10 tooth-shape angle that circumferentially staggers half, the helical gear that the two pairs of engaging gears are the helix angle equal and opposite in direction, rotation direction is opposite, driving shaft cogs and links by key and its axle, driven shaft gear 14 connects with its driven shaft 12 by key, driven shaft gear 16 is enclosed within on its driven shaft, and purpose is for fear of interference.Sweeping thorax by tooth top constitutes tooth top and contacts radial seal with pump case inner chamber arc surface and cooperate.Be provided with seal ring 2,15 between left and right sides end cap and the pump case.
The working principle of mesohigh gear pump and low pressure gear pump is identical, but low pressure pump can not use under mesohigh.Its reason is: because the end clearance and the radial clearance of low pressure gear pump gear all are definite values, after working pressure improved, the leakage rate in its gap increased greatly, and volumetric efficiency is significantly descended (1), so that can not set up mesohigh.(2) along with the raising of working pressure, unbalanced radial force also increases thereupon, so that the bearing cisco unity malfunction.
In the mesohigh gear pump, in order to improve the automatic compensator that volumetric efficiency generally all adopts axial clearance, i.e. " floating pressure side plate ", this pump is adopted as the floating pressure side plate of 8 fonts, as shown in Figure 4.The advantage of this kind compensation device is: because the symmetry center and the master of compensation area, the symmetry center of the end face of follower overlaps, so the line of action of hydraulic pressure impacting force (promptly compensating making a concerted effort of hydraulic coupling) is by the center of floating pressure side plate, the mind-set pumping cavity departs from the side plate and the force action line of the hydraulic pressure reaction thrust of floating pressure side plate opposite side leaves, these two power have just formed couple to side plate, side plate is tilted, not only can increase cellar area, increase and leak, also can make the side plate dumb and local friction of floating, the length of thread engagement of side plate and housing should be strengthened for overcoming above-mentioned shortcoming, and improve precision.
Bearing is one of major part of gear pump, depends primarily on the life-span of used bearing the working life of gear pump, and therefore selecting bearing for use is the critical process of gear pump design, must resolve.The present invention adopts sliding bearing (first-selected DU bearing), and the DU sliding bearing has simple in structure, and is easy for installation, and shock resistance is good, advantages such as operating noise is low, low price.The material of sliding bearing is commonly used bronze, low-tin aluminium alloy, white bearing metal, mock silver and powder metallurgy etc.In recent years, GS-1 polytetrafluoroethylplastic plastic composite material (claiming the DU material abroad) is employed as the gear pump sliding bearing.Because the GS-1 material has the advantage of metal and polytetrafluoroethylplastic plastic concurrently, has favorable mechanical physical property and properties of antifriction and wear resistance, therefore as sliding bearing, have the bearing capacity height, anti-pollution, the serviceability temperature scope is big, long service life, advantages such as low price.Gap length between bearing and axle journal is a very crucial problem.Excesssive gap influences the efficient of pump, too smallly then very easily bearing and axle journal is burnt out.For the general desirable 0.04-0.10mm of sliding bearing gap width, for large discharge pump, the gap of its sliding bearing should be undertaken preferably by repeatedly experiment, to reach long effect of efficient long-life.Select common series for use, inner diameter d=30, outer diameter D=38 chamfering c=0.6 width L=22.For driving shaft, need make multidiameter shaft, be provided with keyway above.
In the design process of pump case, should note the problem of following several respects, must drive oil outlet on (1) pump case.(2) determining of the size of the pump housing (vertically) is subjected to the restriction of several aspects.Because what this pump adopted is the three pieces type structure, thereby the size vertically of pump case is subjected to the restriction of shaft length, and what say here is driven shaft, and for driven shaft is within the pump case fully, thereby its size should be more than or equal to the size of driven shaft.Here be taken as 128mm.Owing on the pump case through hole is arranged, this just needs design wall thickness again; And through hole is φ 18, and pump case should have certain cooperating with left and right sides two end cap, thereby needs the pump housing left and right sides is processed, like this can be well matched, avoid leakage of oil, and the inwall of the pump housing must match with the floating pressure side plate.Thereby quite high machining accuracy must be arranged, and gear must the retaining thorax in movement process.Thereby its machining accuracy is quite high.Between the left and right sides end cap and the pump housing good sealing to be arranged, so just help to realize mesohigh, and require mesohigh district low pressure area to separate.The thickness of seal ring should be consistent with the groove depth on the end cap, can stay the slit between the pump housing and the left and right sides two end cap when too high, bad like this, cross to seal when hanging down and do not have the purpose of isolating mesohigh and low pressure, and it is also meaningless for the sealing of left and right sides two end cap and pump case, its thickness of fitness for purpose is slightly larger than groove depth, and certain decrement is arranged, and is convenient to sealing and isolates.For bag skeleton rotary shaft lip seal in adopting between right end cap and the driving shaft.
Claims (3)
1. asymmetric double circular arc mesohigh gear pump, two ends, the pump case left and right sides are provided with end cap, it is characterized in that: gear is that asymmetric double is arc toothed, profile of tooth is made up of two sections circular arcs, tooth top partly is the dome arc, tooth root partly is a concave circular arc, the tooth-shape angle that circumferentially staggers half of two gears on the driving shaft, be provided with dividing plate between the inner side end of two pairs of gears that are meshing with each other, be provided with the floating pressure side plate that is enclosed within on driving shaft and the driven shaft between the outside end face and the left and right sides end cap, sweep thorax by tooth top and constitute tooth top and contact the radial seal cooperation with pump case inner chamber arc surface.
2. asymmetric double circular arc mesohigh gear pump according to claim 1 is characterized in that: two pairs of pitch wheels, and wherein 2 gears are by key connecting on the driving shaft, and 1 gear is by key connecting on the driven shaft, and another geared sleeve is on driven shaft.
3. asymmetric double circular arc mesohigh gear pump according to claim 2 is characterized in that: the helical gear that the two pairs of engaging gears are the helix angle equal and opposite in direction, rotation direction is opposite.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101052062A CN1316162C (en) | 2003-11-24 | 2003-11-24 | Medium-high pressure gear pump having asymmetric double-circular-arc gear shape |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101052062A CN1316162C (en) | 2003-11-24 | 2003-11-24 | Medium-high pressure gear pump having asymmetric double-circular-arc gear shape |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1544814A true CN1544814A (en) | 2004-11-10 |
| CN1316162C CN1316162C (en) | 2007-05-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003101052062A Expired - Fee Related CN1316162C (en) | 2003-11-24 | 2003-11-24 | Medium-high pressure gear pump having asymmetric double-circular-arc gear shape |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101248276B (en) * | 2005-07-26 | 2010-08-11 | 卡亚巴工业株式会社 | Gear pump |
| CN103267108A (en) * | 2013-05-13 | 2013-08-28 | 浙江大学 | Helical gear with Padovan helix tooth form |
| FR2987406A1 (en) * | 2012-02-27 | 2013-08-30 | Pomtava Sa | PAINT DOSING PUMP |
| CN104361261A (en) * | 2014-12-08 | 2015-02-18 | 中国人民解放军防化学院 | Gear pump health state evaluation method based on profust reliability theory |
| CN104358687A (en) * | 2014-10-30 | 2015-02-18 | 大连交通大学 | Bilinear asymmetric toothed medium-pressure gear pump |
| CN104564660A (en) * | 2015-01-16 | 2015-04-29 | 上海大学 | Low-pulse compound gear pump |
| CN104919181A (en) * | 2012-12-18 | 2015-09-16 | 丹佛斯动力系统有限责任公司 | Geared hydraulic machine and relative gear wheel |
| CN105041638A (en) * | 2015-08-31 | 2015-11-11 | 王志强 | Conveying metering water pump for family heating and metering regulating device of conveying metering water pump |
| CN106593860A (en) * | 2015-10-15 | 2017-04-26 | 通用汽车环球科技运作有限责任公司 | Lubricating fluid system for a vehicle with self compensation plate |
| CN106894991A (en) * | 2017-05-05 | 2017-06-27 | 皮桂庆 | A kind of gear pump of misphase gear collocation structure |
| CN108286517A (en) * | 2018-04-10 | 2018-07-17 | 山西平阳重工机械有限责任公司 | Coupling wheel spiral rotor pump |
| CN108953554A (en) * | 2018-08-06 | 2018-12-07 | 查世樑 | A kind of Novikov gears with double circular arc tooth profiles |
| CN110375054A (en) * | 2019-06-25 | 2019-10-25 | 格特拉克（江西）传动系统有限公司 | A kind of unsymmetric gear design method based on flank profil dip deviation |
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| US3164099A (en) * | 1961-08-09 | 1965-01-05 | Iyoi Hitosi | Toothed profiles of rotors of gear pump |
| GB1232019A (en) * | 1967-09-04 | 1971-05-19 | ||
| GB2135734B (en) * | 1982-09-07 | 1986-01-29 | Ford Motor Co | Helical gear pump |
| US5108275A (en) * | 1990-12-17 | 1992-04-28 | Sager William F | Rotary pump having helical gear teeth with a small angle of wrap |
| GB2311334A (en) * | 1996-03-21 | 1997-09-24 | Ultra Hydraulics Ltd | Gear pump with two out of phase gears on a common shaft. |
| CN2535579Y (en) * | 2001-12-19 | 2003-02-12 | 阜新市北星液压件厂 | Middle high-pressure gear oil-pump |
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2003
- 2003-11-24 CN CNB2003101052062A patent/CN1316162C/en not_active Expired - Fee Related
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101248276B (en) * | 2005-07-26 | 2010-08-11 | 卡亚巴工业株式会社 | Gear pump |
| FR2987406A1 (en) * | 2012-02-27 | 2013-08-30 | Pomtava Sa | PAINT DOSING PUMP |
| WO2013127651A1 (en) * | 2012-02-27 | 2013-09-06 | Pomtava Sa | Paint metering pump |
| CN104919181A (en) * | 2012-12-18 | 2015-09-16 | 丹佛斯动力系统有限责任公司 | Geared hydraulic machine and relative gear wheel |
| CN104919181B (en) * | 2012-12-18 | 2018-04-27 | 丹佛斯动力系统有限责任公司 | Gear hydraulic machine and associated gear |
| CN103267108A (en) * | 2013-05-13 | 2013-08-28 | 浙江大学 | Helical gear with Padovan helix tooth form |
| CN103267108B (en) * | 2013-05-13 | 2015-08-12 | 浙江大学 | There are the helical gear of bar all ten thousand helix profiles of tooth |
| CN104358687A (en) * | 2014-10-30 | 2015-02-18 | 大连交通大学 | Bilinear asymmetric toothed medium-pressure gear pump |
| CN104361261B (en) * | 2014-12-08 | 2017-03-29 | 中国人民解放军防化学院 | A kind of gear pump health state evaluation method theoretical based on profust reliability |
| CN104361261A (en) * | 2014-12-08 | 2015-02-18 | 中国人民解放军防化学院 | Gear pump health state evaluation method based on profust reliability theory |
| CN104564660A (en) * | 2015-01-16 | 2015-04-29 | 上海大学 | Low-pulse compound gear pump |
| CN105041638A (en) * | 2015-08-31 | 2015-11-11 | 王志强 | Conveying metering water pump for family heating and metering regulating device of conveying metering water pump |
| CN106593860A (en) * | 2015-10-15 | 2017-04-26 | 通用汽车环球科技运作有限责任公司 | Lubricating fluid system for a vehicle with self compensation plate |
| US10018083B2 (en) | 2015-10-15 | 2018-07-10 | GM Global Technology Operations LLC | Lubricating fluid system for a vehicle with self compensation plate |
| CN106593860B (en) * | 2015-10-15 | 2019-11-08 | 通用汽车环球科技运作有限责任公司 | Vehicle lubrication fluid system with self compensation plate |
| CN106894991A (en) * | 2017-05-05 | 2017-06-27 | 皮桂庆 | A kind of gear pump of misphase gear collocation structure |
| CN108286517A (en) * | 2018-04-10 | 2018-07-17 | 山西平阳重工机械有限责任公司 | Coupling wheel spiral rotor pump |
| CN108953554A (en) * | 2018-08-06 | 2018-12-07 | 查世樑 | A kind of Novikov gears with double circular arc tooth profiles |
| CN110375054A (en) * | 2019-06-25 | 2019-10-25 | 格特拉克（江西）传动系统有限公司 | A kind of unsymmetric gear design method based on flank profil dip deviation |
| CN110375054B (en) * | 2019-06-25 | 2022-07-08 | 麦格纳动力总成(江西)有限公司 | Asymmetric gear design method based on tooth profile inclination deviation |
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| CN1316162C (en) | 2007-05-16 |
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Granted publication date: 20070516 |