CN101705937A - Skewed tooth gear pump - Google Patents
Skewed tooth gear pump Download PDFInfo
- Publication number
- CN101705937A CN101705937A CN200910236644A CN200910236644A CN101705937A CN 101705937 A CN101705937 A CN 101705937A CN 200910236644 A CN200910236644 A CN 200910236644A CN 200910236644 A CN200910236644 A CN 200910236644A CN 101705937 A CN101705937 A CN 101705937A
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- curve
- helical gear
- tooth
- pump
- gear pump
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Abstract
The invention discloses a skewed tooth gear pump, which belongs to the field of mechanical rotor pumps. The technical scheme is that the skewed tooth gear pump comprises a pump body (6), an oil suction port (7) formed on the pump body (6), an oil outlet (8), and a driving skewed tooth cylindrical gear (1) and a driven skewed tooth cylindrical gear (2) which are meshed with each other in a fixed speed ratio in the pump body (6), wherein the end face profile curves of the driving and driven skewed tooth cylindrical gears (1) and (2) are the same and consist of an involute (3), a tooth crest curve (4) and a tooth root curve (5); and the tooth crest curve (4) is a continuous smooth symmetrical curve and is tangential with the involute (3), and the tooth root curve (5) is a conjugate curve of the tooth crest curve (4). The skewed tooth gear pump adopts full tooth profile conjugate continuous transmission in the fixed speed ratio, and is the skewed tooth gear pump with fewer teeth, large delivery capacity, less internal leakage, low noises and stable running.
Description
Technical field
The present invention relates to a kind of helical gear pump, belong to mechanical rotor pump field, particularly the gear pump technical scope.
Technical background
Gear pump is owing to simple in structure, conveying that reliable operation is widely used in oily fluid, build pressure, in recent years in design of Hydraulic System, can save manufacture cost significantly by the helical gear pump replacement servo variable displacement pump that driven by servomotor or frequency control motor drive, have tangible power savings simultaneously.Require in this system that the angular gear pump displacement that disposed is big, volumetric efficiency is high, so that wide, the pressure stability of flow rate of hydraulic system output area realizes the accurate control of each feature of hydraulic system and performance parameter; Various gear pumps in the market all can not satisfy above requirement, because the low accurate control that can not satisfy trace output of its volumetric efficiency.Reduce the gear number of teeth or increase axial length and can strengthen the angular gear pump delivery, but can not satisfying very little the time, the gear number of teeth builds the pressure output condition continuously, let out in causing, volumetric efficiency descends, changing helical gear transverse tooth profile curve shape can influence angular gear pump delivery and volumetric efficiency; In the real work helical gear pump manufactured and designed and proposed requirements at the higher level.
Summary of the invention
The objective of the invention is to provide a kind of few number of teeth, big discharge capacity helical gear pump, by strengthening the helical gear Face contact ratio ε of pair of meshing
βSatisfy continuous transmission condition, satisfy air-proof condition by changing the helical gear tooth curve.
In order to reach purpose of the present invention, the technological scheme of being taked comprises the pump housing 6, is positioned at the active helical gear 1 and the driven helical gear 2 of inlet port 7, oil outlet 8 and the pump housing 6 speed ratio engagements decided at the higher level but not officially announced on the pump housing 6, the transverse tooth profile curve of driving and driven helical gear 1,2 is identical, constitute by involute 3, tip curve 4,5 three sections curves of tooth root curve, tip curve 4 for smooth continuously are conjugate curve of tip curve 4 about tooth center line symmetrical curve and, tooth root curve 53 tangent with involute, the pump housing 6 die cavity center of arc are apart from o
1o
2=a, driving and driven helical gear 1,2 parallel axes are rotated in the pump housing 6 speed ratio engagements decided at the higher level but not officially announced with reference center distance a, constitute a kind of helical gear pump (as Fig. 1); Driving and driven helical gear 1,2 satisfy the wide conjugate condition of full-depth tooth, satisfy constant speed than condition i by the involute 3 of tooth curve
12=c (constant) and continuous transmission condition ε=ε
α+ ε
β＞1, satisfy the air-proof condition of helical gear pump by the wide conjugate condition of the full-depth tooth of tooth curve.
In the above-mentioned helical gear pump, driving and driven helical gear 1,2 have identical transverse module m, pressure angle α (or normal module m
n, pressure angle α
n), helixangle equates that rotation direction is opposite, the transverse tooth profile curve is identical, the identical (z of driving and driven helical gear 1,2 numbers of teeth
1=z
2=constitute with number of teeth helical gear pump two helical gear number of teeth difference (z z) time
1≠ z
2) time constitute different number of teeth helical gear pump, can realize that all the wide conjugation of full-depth tooth, constant speed are than continuous transmission when reference center distance a installs separately.
In the above-mentioned helical gear pump, tip curve 4 is designed to circular arc, the center of circle on tooth center line oy in the transverse tooth profile curve of driving and driven helical gear 1,2, the point of contact of circular arc and involute 3 is A (as Fig. 3), and tooth root curve 5 is conjugate curve of circle-arc tooth summit curve 4; Form the transverse tooth profile curve of driving and driven helical gear 1,2 by the conjugate curve BD of involute section AB, circular arc AC and circular arc AC, reference center distance a satisfies the wide conjugation of full-depth tooth, the constant speed helical gear pump operating conditions than continuous transmission when installing.
In the above-mentioned helical gear pump, tip curve 4 is designed to ellipse, minor axis on tooth center line oy in the transverse tooth profile curve of driving and driven helical gear 1,2, oval point of contact with involute 3 is A (as Fig. 4), and tooth root curve 5 is conjugate curve of oval tip curve 4; Form the transverse tooth profile curve of driving and driven helical gear 1,2 by the conjugate curve BD of involute section AB, oval AC and oval AC, reference center distance a satisfies the wide conjugation of full-depth tooth, the constant speed helical gear pump operating conditions than continuous transmission when installing.
In the above-mentioned helical gear pump, tip curve 4 is dot encapsulations with the die cavity circular arc of the pump housing 6 in the transverse tooth profile curve of driving and driven helical gear 1,2, along axis is the helix sealing, change the relative curvature of seal point (line) by the linear or parameter of curve that changes tip curve 4, so that change sealing characteristics, and then reduce tooth top wearing and tearing, increase helical gear pump working life.
The invention has the beneficial effects as follows: the wide conjugation of full-depth tooth, constant speed can realize few number of teeth, big discharge capacity than the helical gear pump of continuous transmission, and internal leakage is few, noise is little, smoothness of operation is good, satisfies the accurately helical gear pump of control of flow.
Description of drawings
Fig. 1 is the helical gear pump schematic diagram;
Fig. 2 is the helical gear theory of engagement figure of helical gear pump;
Fig. 3 tip curve is the helical gear transverse tooth profile curve theory of constitution figure of circular arc;
Fig. 4 tip curve is oval helical gear transverse tooth profile curve theory of constitution figure;
Fig. 5 is a helical gear pump structural principle graphics.
Specific embodiments
With reference to the accompanying drawings embodiments of the invention are described below.
Helical gear pump shown in Figure 1 is made up of the pump housing 6, the active helical gear 1 and the driven helical gear 2 that are positioned at inlet port 7 on the pump housing 6, oil outlet 8 and the pump housing 6 speed ratios engagements decided at the higher level but not officially announced, the transverse tooth profile curve of driving and driven helical gear 1,2 is identical, constitute by involute 3, tip curve 4,5 three sections curves of tooth root curve, tip curve 4 for smooth continuously are conjugate curve of tip curve 4 about tooth center line symmetrical curve and, tooth root curve 53 tangent with involute; Driving and driven helical gear 1,2 have identical transverse module m, pressure angle α (or normal module m
n, pressure angle α
n), the long b of axial direction tooth, helixangle equates that rotation direction is opposite, initiatively helical gear 1 be that left-handed, driven helical gear 2 are dextrorotation (as Fig. 2); Identical (the z of driving and driven helical gear 1,2 numbers of teeth
1=z
2=constitute with number of teeth helical gear pump driving and driven helical gear 1,2 number of teeth difference (z z) time
1≠ z
2) time constitute different number of teeth helical gear pump; For common same number of teeth helical gear pump (z
1=z
2=z), reference radius r=mz/2, Base radius r
b=mzcos α/2, reference center distance a=mz, contact ratio ε=ε
α+ ε
β＞1, present embodiment is with number of teeth helical gear pump z=7, changes Face contact ratio ε by adjusting long b of axial direction tooth and helixangle
β, make ε＞1 satisfy continuous transmission condition; The pump housing 6 die cavity center of arc are apart from o
1o
2=a, driving and driven helical gear 1,2 parallel axes are rotated (as Fig. 5) with reference center distance a in the pump housing 6 speed ratio engagements decided at the higher level but not officially announced; Because the transverse tooth profile curve of driving and driven helical gear 1,2 is identical, two gear face tooth curves engagement during gear pump work, the involute section of two gear-profile curves is conjugation, initiatively the tip curve of helical gear 1 and the tooth root curve of driven helical gear 2 are conjugation, initiatively the tooth root curve of helical gear 1 and the tip curve of driven helical gear 2 are conjugation, and therefore driving and driven helical gear 1,2 satisfy the wide conjugate condition of full-depth tooth; Involute 3 by tooth curve satisfies constant speed than condition i
12=c (constant) and continuous transmission condition ε=ε
α+ ε
β＞1, satisfy the air-proof condition of helical gear pump by the wide conjugate condition of the full-depth tooth of tooth curve, driving and driven helical gear 1,2 install to realize that by reference center distance a the wide conjugation of full-depth tooth, constant speed are than continuous transmission. the wide conjugation helical gear pump of full-depth tooth Design Theory be no sideshake, no bottom clearance, consider distortion that the pressure difference of thermal expansion, oil inlet and outlet causes etc. in conjunction with the viscosity of conveyance fluid by manufacturing tolerances provide required between the crack with the proper functioning of guarantee gear pump.
Tip curve shown in Figure 3 is among the helical gear transverse tooth profile curve theory of constitution figure of circular arc, tip curve 4 is designed to circular arc, the center of circle on tooth center line oy in the transverse tooth profile curve of driving and driven helical gear 1,2, the point of contact of circular arc and involute 3 is A, satisfy smooth continuously symmetrical curve and tangent with involute 3, tooth root curve 5 is conjugate curve of circle-arc tooth summit curve 4.Two gear face tooth curves engagement during gear pump work, initiatively the tooth root curve of helical gear 1 and the circle-arc tooth summit curve of driven helical gear 2 are conjugation, because the transverse tooth profile curve of driving and driven helical gear 1,2 is identical, so initiatively the tooth root curve of helical gear 1 is the conjugate curve of its own circle-arc tooth summit curve; In like manner, the circle-arc tooth summit curve of the tooth root curve of driven helical gear 2 and active helical gear 1 is a conjugation, because the transverse tooth profile curve of driving and driven helical gear 1,2 is identical, so the tooth root curve of driven helical gear 2 is conjugate curve of its own circle-arc tooth summit curve; Conjugate condition can be described as two curve continuous phase cut-graftings and touches, and vector equation is: n
1=n
2, r
2=r
1+ o
21, n
1V
12=0, wherein: r
1, r
2Be two gear face tooth curve point of contact radius vectors, n
1, n
2Be point of contact two curve per unit system vectors, v
12Be the relative velocity vector of point of contact two gears, o
21Be centre distance o
2o
1Vector; Form the transverse tooth profile curve of driving and driven helical gear 1,2 by the conjugate curve BD of involute section AB, circular arc AC and circular arc AC, reference center distance a satisfies the wide conjugation of full-depth tooth, the constant speed helical gear pump operating conditions than continuous transmission when installing.
Tip curve shown in Figure 4 is among the helical gear transverse tooth profile curve theory of constitution figure of ellipse, tip curve 4 is designed to ellipse, minor axis on tooth center line oy in the transverse tooth profile curve of driving and driven helical gear 1,2, oval point of contact with involute 3 is A, satisfy smooth continuously symmetrical curve and tangent with involute 3, tooth root curve 5 is conjugate curve of oval tip curve 4; Form the transverse tooth profile curve of driving and driven helical gear 1,2 by the conjugate curve BD of involute section AB, oval AC and oval AC, reference center distance a satisfies the wide conjugation of full-depth tooth, the constant speed helical gear pump operating conditions than continuous transmission when installing.Tip curve 4 is dot encapsulations with the die cavity circular arc of the pump housing 6 in the transverse tooth profile curve of driving and driven helical gear 1,2, along axis is the helix sealing, change the relative curvature of seal point (line) by the linear or parameter of curve that changes tip curve 4, so that change sealing characteristics, and then reduce tooth top wearing and tearing, increase helical gear pump working life.
It should be noted last that, above embodiment is only unrestricted in order to technological scheme of the present invention to be described, although the present invention is had been described in detail with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement technological scheme of the present invention, and not breaking away from the spirit and scope of technical solution of the present invention, it all should be encompassed in the middle of the claim scope of the present invention.
Claims (3)
1. a helical gear pump comprises the pump housing (6), be positioned at the inlet port (7) on the pump housing (6), the active helical gear (1) and the driven helical gear (2) of the speed ratio engagement decided at the higher level but not officially announced of the oil outlet (8) and the pump housing (6), it is characterized in that, initiatively helical gear (1) are identical with the transverse tooth profile curve of driven helical gear (2), by involute (3), tip curve (4), tooth root curve (5) constitutes, tip curve (4) is continuously smooth about tooth center line symmetrical curve and tangent with involute (3), tooth root curve (5) is the conjugate curve of tip curve (4), and initiatively helical gear (1) and driven helical gear (2) parallel axes are with the wide conjugation of reference center distance a full-depth tooth in the pump housing (6), constant speed is than engagement rotation continuously.
2. helical gear pump according to claim 1, it is characterized in that, constitute with the number of teeth helical gear pump when initiatively the number of teeth of helical gear (1) and driven helical gear (2) is identical, the two helical gear numbers of teeth do not constitute different number of teeth helical gear pump simultaneously.
3. helical gear pump according to claim 1 and 2, it is characterized in that, initiatively tip curve (4) is designed to circular arc, the center of circle on the tooth center line in the transverse tooth profile curve of helical gear (1) and driven helical gear (2), circular arc and involute (3) are tangent, and tooth root curve (5) is the conjugate curve of circle-arc tooth summit curve (4); Perhaps tip curve (4) is designed to ellipse, minor axis on the tooth center line in the transverse tooth profile curve of active helical gear (1) and driven helical gear (2), oval tangent with involute (3), tooth root curve (5) is the conjugate curve of oval tip curve (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910236644A CN101705937A (en) | 2009-11-04 | 2009-11-04 | Skewed tooth gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910236644A CN101705937A (en) | 2009-11-04 | 2009-11-04 | Skewed tooth gear pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101705937A true CN101705937A (en) | 2010-05-12 |
Family
ID=42376183
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910236644A Pending CN101705937A (en) | 2009-11-04 | 2009-11-04 | Skewed tooth gear pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101705937A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322419A (en) * | 2011-09-30 | 2012-01-18 | 浙江奥威特液压机械有限公司 | Screw pump |
| CN103732340A (en) * | 2011-07-29 | 2014-04-16 | 格里森工场 | Optimization of face cone element for spiral bevel and hypoid gears |
| CN103925352A (en) * | 2014-03-31 | 2014-07-16 | 西安理工大学 | Same-direction meshing conjugate tooth profile pair and construction method |
| CN104832622A (en) * | 2015-05-20 | 2015-08-12 | 蒋桂云 | Harmonic reducer of improved structure |
| CN104948450A (en) * | 2015-05-29 | 2015-09-30 | 重庆红宇精密工业有限责任公司 | Oil pump rotor |
| CN105649976A (en) * | 2015-12-29 | 2016-06-08 | 西安航天动力研究所 | Micro different-tooth-number high-speed magnetic-driving electric gear pump |
| CN106762612A (en) * | 2017-01-10 | 2017-05-31 | 黄山工业泵制造有限公司 | A kind of high-pressure spiral gear pump with gapless external toothing tooth form |
| CN108374787A (en) * | 2018-05-03 | 2018-08-07 | 重庆潍柴发动机有限公司 | A kind of gear pump structure and its design method for realizing that left and right favourable turn is general |
| CN109026677A (en) * | 2018-08-28 | 2018-12-18 | 金迈思液压设备（天津）有限公司 | A kind of repairing type helical gear and the helical gear axle sleeve, pressure end cap, gear pump |
| CN115142645A (en) * | 2021-03-31 | 2022-10-04 | 广东博智林机器人有限公司 | Liquid material uniform distribution device and liquid material coating robot |
-
2009
- 2009-11-04 CN CN200910236644A patent/CN101705937A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103732340A (en) * | 2011-07-29 | 2014-04-16 | 格里森工场 | Optimization of face cone element for spiral bevel and hypoid gears |
| CN102322419A (en) * | 2011-09-30 | 2012-01-18 | 浙江奥威特液压机械有限公司 | Screw pump |
| CN102322419B (en) * | 2011-09-30 | 2016-01-20 | 浙江奥威特液压机械有限公司 | Screw pump |
| CN103925352A (en) * | 2014-03-31 | 2014-07-16 | 西安理工大学 | Same-direction meshing conjugate tooth profile pair and construction method |
| CN104832622A (en) * | 2015-05-20 | 2015-08-12 | 蒋桂云 | Harmonic reducer of improved structure |
| CN104948450A (en) * | 2015-05-29 | 2015-09-30 | 重庆红宇精密工业有限责任公司 | Oil pump rotor |
| CN105649976A (en) * | 2015-12-29 | 2016-06-08 | 西安航天动力研究所 | Micro different-tooth-number high-speed magnetic-driving electric gear pump |
| CN106762612A (en) * | 2017-01-10 | 2017-05-31 | 黄山工业泵制造有限公司 | A kind of high-pressure spiral gear pump with gapless external toothing tooth form |
| CN108374787A (en) * | 2018-05-03 | 2018-08-07 | 重庆潍柴发动机有限公司 | A kind of gear pump structure and its design method for realizing that left and right favourable turn is general |
| CN109026677A (en) * | 2018-08-28 | 2018-12-18 | 金迈思液压设备（天津）有限公司 | A kind of repairing type helical gear and the helical gear axle sleeve, pressure end cap, gear pump |
| CN115142645A (en) * | 2021-03-31 | 2022-10-04 | 广东博智林机器人有限公司 | Liquid material uniform distribution device and liquid material coating robot |
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Application publication date: 20100512 |