CN201496509U - Male and female full rolling gear - Google Patents

Male and female full rolling gear Download PDF

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Publication number
CN201496509U
CN201496509U CN2008201308363U CN200820130836U CN201496509U CN 201496509 U CN201496509 U CN 201496509U CN 2008201308363 U CN2008201308363 U CN 2008201308363U CN 200820130836 U CN200820130836 U CN 200820130836U CN 201496509 U CN201496509 U CN 201496509U
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CN
China
Prior art keywords
gear
tooth
transmission
circle
rolling curve
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Expired - Fee Related
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CN2008201308363U
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Chinese (zh)
Inventor
赖登桂
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Individual
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Individual
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Priority to CN2008201308363U priority Critical patent/CN201496509U/en
Priority to PCT/CN2009/072774 priority patent/WO2010006550A1/en
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Publication of CN201496509U publication Critical patent/CN201496509U/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling

Abstract

A male and female full rolling gear belongs to mechanical transmission gears. In a generally known involute gear, the tooth profiles of a driver gear and a driven gear are contacted and transmitted in the convex direction. The utility model provides a gear of which the two tooth profile curves of the driver gear and the driven gear are contacted and transmitted in a matched concave-convex manner, the contact line of engagement lies in two intersectant lines of centers, the pressure angles of the contact and transmission points are both zero, the tooth profile angles are 45 DEG, the tooth height h is one half of t (circular pitch), and the crown circle is a pitch circle. From the practical detection of a reducer equipped with the gear, when the input power is 5.5 KW, the mechanical efficiency reaches 95.8 percent; and when the input power is increased to 7.5 KW, the mechanical efficiency reaches 97 percent without sliding friction, impact, vibration or noise but a temperature increment of 14 DEG C, therefore, the gear not only suits the gear transmission of common machinery, but also better suits the gear transmission of the machinery with high power and speed.

Description

The full rolling bearing of negative and positive
Technical field
The full rolling bearing of negative and positive belongs to mechanical drive gear.The present invention develops on the basis with involute gear, continues to use it and uses noun, term.
Background technique
The modern involute gear more generally that adopts is a tooth curve with the involute, and two gear-profile Contact Transmission line of contact are internal common tangents of two rolling circles.Two gears are in the transmission operation process, and the every bit in two gears is all being made circular movement, and the transmission point of contact is no exception, are not the point of contacts of two circles, are exactly the intersection point of two circles, and only the contact points on the line of centers of two fixing circles is only the point of contact of two circles.Involutes Gears Transmission has only click-through to cross line of centers, and this point is the node on the involute gear pitch circle, and remaining contact is all outside the line of centers of two gears circle, all be the intersection point of two circles, must produce sliding friction, produce impact, vibration and noise, it is higher to heat up, and mechanical efficiency is lower.
Tooth wheel is a flank profil with all diametal curves, but the same with the involute gear protruding tooth Profile Design outside the tooth sideline of driving wheel flank profil with the follower flank profil, though mechanical efficiency is than involute gear height, solved the sliding friction problem, but because of do not solve this curve vector direction with protruding to protruding to contacting the interference problem, impact, vibration and noise are still arranged, and mechanical efficiency is not high.
Circular tooth gear, circular tooth gear are the concavo-convex transmission of joining to the eye, but the flank profil of circular tooth gear is a circular arc, and the contact line of contact is a line segment, have only a point by line of centers, and remaining contact contact points is the intersection point of two circles, must produce sliding friction.In addition, its contact engagement is positive Contact Transmission, rather than the side, point tolerance is arranged even only rolling point does not all contact if make precision, promptly produces sliding friction and impact, and vibration is if the contact interference just produces bigger resistance.
Summary of the invention
Of the present utility model is the defective that overcomes above-mentioned all gears, provides a kind of do not have sliding friction, no impact, vibration, noise, the null full rolling negative and positive rolling bearing of pressure angle.
The roll full technological scheme of negative and positive rolling bearing of the utility model is: two engagement driving gears, a gear-profile rolling curve is protruding outside the tooth sideline, another gear-profile rolling curve is concavity, engagement driving becomes concavo-convex Contact Transmission, the contact line of contact is on the line of centers that intersects of two gears circle, the tooth curve of gear is that circle is gone up a bit and not only to be made circular movement but also to make the track that the radial alignment motion synthesized to become rolling curve, pressure angle equals zero, its tooth-shape angle is 45 °, tooth depth h=t/2, top circle are pitch circle.
When two meshed transmission gear, the tooth top of gearwheel and the tooth root of small gear join, the tooth top of small gear and the tooth root of gearwheel join, the flank profil of general gearwheel is a sag vertical curve, the flank profil of small gear is a convex curve, the equal key elements that the two curve vector moulds that so both met two circles equate, direction is identical realize the negative and positive continuous rolling that is harmonious in transmission process, solved the resistance problem that produces when two convex curves meet again.
Top circle is that pitch circle is meant that the top circle circular pitch of big or small two gears equates, certainly its 1/2 circular pitch also equates, when two gear transmissions were turned round, the circular pitch when the gearwheel tooth top contacts to next gearwheel tooth top with the small gear tooth root equated with the circular pitch of pinion head to next tooth top.Because the transmission point of contact of big small gear be from tooth root to tooth top again from tooth top to tooth root.On the contact line of contact line of centers that promptly two gears circle intersects, walk up and down.
Gear of the present utility model is when engagement driving, the tooth top of gearwheel and the tooth root of small gear join, the tooth top of small gear and the tooth root of gearwheel join, the circular pitch t of two gears equates, radial alignment is that tooth depth h equates, the rolling curve vector of two circles, " when the mould of two vectors was identical with direction, this two vector equated according to the engineering mathematics analysis." and two tooth curves are concavo-convex is harmonious, and one-to-one relationship is arranged, and transmission continuously, rolling.In the quick transmission of two gears in a flash, realize the face Contact Transmission, mechanical efficiency reaches 97% height during experimental test.
Description of drawings
Fig. 1 is the schematic representation of the full rolling bearing of negative and positive.
Fig. 2 is the title and the code name schematic representation at each position of the full rolling bearing of negative and positive.
Fig. 3 is negative and positive roll full straight-tooth dish angle tooth and transmission shaft transmission schematic representation.
Transmission shaft and dish angle tooth schematic representation that Fig. 4 rolls entirely and is with helical teeth for negative and positive.
Fig. 5 is the negative and positive straight umbrella tooth of the straight-tooth schematic representation that rolls entirely.
Fig. 6 is the negative and positive planetary pinion schematic representation that rolls entirely.
Fig. 7 is designed for the rolling bearing structure schematic representation for the full rolling bearing of negative and positive.
Fig. 8 is the negative and positive helical gear structural representation that rolls entirely.
Embodiment
As shown in Figure 1, be the utility model design principle structural representation, figure middle gear O 1Root circle 1, double wedge 2, gear O 2 Top circle 3, gear O 1 Top circle 4, gear O 2Root circle 5, line of centers 6, gear O 2Recessed flank profil 7.Two engagement driving gears, the protruding double wedge 2 that outside the tooth sideline, forms of gear-profile rolling curve, another gear-profile curve is concavity and forms recessed flank profil 7, engagement driving becomes concavo-convex Contact Transmission, and the contact line of contact is on the line of centers 6 that intersects of two gears circles, and the tooth curve of gear is that circle is gone up a bit and not only to be made circular movement but also to make the track that the radial alignment motion synthesized to become rolling curve, pressure angle equals zero, its tooth-shape angle is 45 °, tooth depth h=t/2, and top circle 3,7 is a pitch circle.
Be illustrated in figure 2 as the title and the code name of each one of the utility model negative and positive rolling bearing
Top circle---the circle that tooth top is all, diameter is represented (this gear is decided to be pitch circle) with de.
Root circle---the circle that tooth root is all, diameter is represented with di.
Standard pitch circle---the circle in the middle of top circle and root circle is represented with d.
Transverse tooth thickness---the arc length of gear teeth the right and left on standard pitch circle represented with S.
Between cog---adjacent about the arc length of space on standard pitch circle between two flank profils represent with W.W＞S
Addendum---the gear compound graduation circle is represented with he to the radial distance of top circle.
Dedendum of the tooth---root circle is represented with hi to the radial distance of standard pitch circle.
Whole depth---top circle is represented h=he+hi to the radial distance of root circle with h.
The facewidth---the gear width at axial direction is represented with B.
The major parameter of the utility model rolling bearing
The tip diameter d of (one) modulus---gear, circular pitch t and number of teeth z, exist the following t=of relation л d/z be t/ л=d/z wherein t/ л be taken as the basic parameter of rational as gear, be called modulus, represent that with m there is a t/ л millimeter in unit for millimeter.
The former angle that moving direction became that means power thrusts and object of (two) pressure angle---pressure angle.In the engaging gear of a pair of Contact Transmission, the power thrusts of driving wheel is the tangent direction of this point of contact, and driven wheel also is a tangent direction in the moving direction of this point.Because driving wheel and driven wheel all are circular movement, thus consistent in the moving direction of this point of contact at the power thrusts of Contact Transmission point with driven wheel, so pressure angle equals zero.The negative and positive rolling bearing with the gear of the contact transmitted power that rolls in its pressure angle all equal zero.But exist in the gear of sliding friction Contact Transmission at other and just not all to equal zero.In involute gear, have only the node on the pitch circle to equal zero.
(3) tooth-shape angle---this rolling bearing tooth-shape angle refers to that the tangent line put on the tooth curve and the angle that radial line became of this point are 45 °.Professional rolling curve is circular movement and the synthetic track of radial alignment motion, and it is that round tangent direction becomes 90 ° with radial line that the point on the tooth angle is made the circular movement direction, by closing of two vectors angle at 45.
(4) number of teeth---the number of teeth is determined that by velocity ratio the gear ratio steamboat knuckle-tooth number of gearwheel circle is many.If axis of great circle is d 1, the number of teeth is Z 1, the steamboat circular diameter is d 2, the number of teeth is Z 2, d is arranged 1/ d 2=Z 1/ Z 2=t (velocity ratio), then d 1/ Z 1=d 2/ Z 2(modulus).
Negative and positive rolling bearing size is calculated
By the diameter of gear-driven velocity ratio and big small gear, make the number of teeth of big small gear.If driving gear O 1, diameter d 1, the number of teeth is Z 1Driven wheel O 2, diameter is d 2, the number of teeth is Z 2, same modulus is M, and same circular pitch is t, and tooth depth is h, and following relation is arranged; By modulus formula M=t/ л, t=л m makes high h=t/2=л m/2 by rolling curve character.Centre distance A is the distance of the two axial lines of pair of meshing two gears, and after correct the installation, it also is two reference radius sums, i.e. A=(d that its line of centers is centre distance A 1+ d 2)/2.
Embodiment 1, is the helical gear of negative and positive rolling bearing, and the driving wheel flank profil is protruding rolling curve, and the driven wheel flank profil is recessed rolling curve (please refer to Fig. 1).
Negative and positive rolling spur gear can be realized the face Contact Transmission, relatively establishes to be used for high-speed big load transmission, but when the transmission of utmost point low speed, contacts with stress surface because it is the power face, and another side is to be rotated by inertial force, generally is discontiguous.At this moment adopt the helical gear transmission.
Embodiment 2, are negative and positive rolling bearing transmission shaft spur gear and dish angle tooth transmission as shown in Figure 3, transmission shaft spur gear 1, rolling bearing 2, dish angle tooth cylindrical 3, dish angle tooth 4.Transmission shaft spur gear 1 flank profil adopts protruding rolling curve, and dish angle tooth 4 adopts recessed rolling curve.
The outer ring circle of making dish angle straight-tooth is tangent with transmission shaft straight-tooth great circle; The tail end circle of transmission shaft straight-tooth is tangent with the inner ring circle of dish angle straight-tooth.The section of rack of transmission shaft is made taper shape, for dish angle tooth tight contact matching, the interior circle of dish angle tooth will increase.The great circle d of disk like this Big by 1Great circle d with transmission shaft Little by 1Tangent, obtain identical circular pitch and modulus and tooth number Z separately according to velocity ratio Big by 1And Z Big by 2, but the spur rack number of teeth on the axle, the number of teeth of both big end and small end is the same Z of being called 1The number of teeth of dish angle tooth great circle and roundlet also is the same, is called Z 2Dish angle gear great circle circle d Big by 1Circular pitch t Greatly=л d Big by 1/ Z 2Dish angle gear ringlet circular pitch is t 2=л d Big by 2/ Z 2Its tooth depth h Greatly=1/2 t Greatly, h Little=1/2t 2Transmission shaft tooth and dish angle tooth close engagement driving like this.
Embodiment 3, are the angle tooth transmission of negative and positive rolling helical teeth dish as shown in Figure 4, and its shaft gear and dish angle tooth are helical teeth shapes, and transmission shaft 1 flank profil adopts protruding rolling curve, and dish angle tooth 2 is recessed rolling curve.
In order to make transmission shaft and dish angle tooth continuous transmission, the transmission shaft tooth be helical teeth when transmission shaft is cone, its oblique line is a helix.
Embodiment 4, are the transmission of negative and positive rolling umbrella gear as shown in Figure 5, and bevel pinion 2 flank profils are protruding rolling curves, and large bevel gear 1 profile of tooth is recessed rolling curve.Similar with the tooth transmission of straight dish angle, different is that two umbrella gear axis of umbrella gear transmission intersect certain angle number; The angle tooth transmission of straight dish, dish corner tooth shaft line and driving cog circumference intersect vertically, and the great circle of large bevel gear 1 and bevel pinion 2 great circles are tangent; Large bevel gear 1 roundlet and bevel pinion 2 roundlets are tangent.
Embodiment 5, are illustrated in figure 6 as the transmission of negative and positive rolling planetary pinion, and planetary pinion flank profil 2 is protruding rolling curve, and the flank profil of great circle internal gear 1 is recessed rolling curve.
Embodiment 6, are illustrated in figure 7 as negative and positive rolling rolling bearing.The external frame of rolling element 3 is protruding rolling curve, and corresponding bearing outer ring 1, bearing inner race 2 are recessed rolling curve with rolling element 3 contacting parts.
There is not sliding friction in the utility model negative and positive rolling bearing, no surface friction drag, be fit to high-power, high-speed mechanical transmission, practice detects when speed reducer input power 7.5KW, mechanical efficiency reaches 97%, so it is suitable for various mechanical transmission, is not only applicable to speed reducer, more is applicable to high-speed overload automobile, aircraft, steamer, large size machine tool, forklift or the like.Its embodiment is by former type gear position size, rolling bearing.If speed reducer can a tractor serves several purposes 5.5KW speed reducer, can be used for the higher speed reducer of 7.5KW or power.The aircraft of running at high speed, train, electric car must stay the increase of speed, the increase of inertial force, must suitably reduce the power of input during design, this has just realized energy-conservation, and simultaneously in order to avoid speed is too fast, inertial force is bigger, lose control of and run at high speed, want speed limit surely, promptly do not surpass former locomotive maximum speed.The velocity ratio design of original gear is big, the tip diameter d of small gear, л d/z (circular pitch) t/ л=d/z (modulus) of circular pitch t=.Make hobcutter at this two tooth-formation of gear and design, the full rolling bearing of production negative and positive on the gear hobbing machine of original production involute, other various gears are by the design proposal of its original production routine in conjunction with new gear, the full rolling bearing of production negative and positive.

Claims (6)

1. the full rolling bearing of negative and positive, it is characterized in that: two engagement driving gears, a gear-profile rolling curve is protruding outside the tooth sideline, and another gear-profile rolling curve is concavity, and engagement driving becomes concavo-convex Contact Transmission, the contact line of contact is on the line of centers that intersects of two gears circle, the tooth curve of gear is that circle is gone up a bit and not only to be made circular movement but also to make the track that the radial alignment motion synthesized to become rolling curve, and pressure angle equals zero, and its tooth-shape angle is 45 °, tooth depth h=t/2, top circle are pitch circle.
2. the full roller gear of negative and positive according to claim 1 is characterized in that described gear is the helical gear transmission, and the driving wheel flank profil is protruding rolling curve, and the driven wheel flank profil is recessed rolling curve.
3. the full roller gear of negative and positive according to claim 1 is characterized in that described gear is transmission shaft and dish angle tooth transmission, and the transmission shaft flank profil adopts protruding rolling curve, and dish angle flank profil adopts recessed rolling curve.
4. the full roller gear of negative and positive according to claim 3 is characterized in that described transmission shaft and dish angle tooth are helical teeth shapes, and the transmission shaft flank profil adopts protruding rolling curve, and dish angle flank profil is recessed rolling curve.
5. the full roller gear of negative and positive according to claim 1 is characterized in that described gear is the umbrella gear transmission, and the umbellule flank profil is protruding rolling curve, and the gamp flank profil is recessed rolling curve.
6. the full roller gear of negative and positive according to claim 1 or 5 is characterized in that described gear is the planetary pinion transmission, and the great circle internal gear tooth is recessed rolling curve, and the planetary pinion flank profil is protruding rolling curve.
CN2008201308363U 2008-07-16 2008-07-16 Male and female full rolling gear Expired - Fee Related CN201496509U (en)

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CN2008201308363U CN201496509U (en) 2008-07-16 2008-07-16 Male and female full rolling gear
PCT/CN2009/072774 WO2010006550A1 (en) 2008-07-16 2009-07-15 Male and female full rolling gears

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105422795A (en) * 2015-11-17 2016-03-23 南京航空航天大学 Conical ring surface involute gear and machining method thereof
CN114987384A (en) * 2021-03-01 2022-09-02 株式会社东海理化电机制作所 Webbing retractor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011013245A1 (en) * 2011-03-07 2012-09-13 Createc Fischer & Co. Gmbh Device for a vacuum and for transmitting or allowing a movement
DE102012004082B4 (en) * 2012-02-29 2014-02-13 Createc Fischer & Co. Gmbh Device for a vacuum and for transmitting or allowing a movement

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1063750A (en) * 1991-09-08 1992-08-19 赖登桂 Tooth wheel
CN2298371Y (en) * 1996-12-24 1998-11-25 中国纺织大学 Convex-concave, convex-plane tooth face meshed gear pair
CN2446333Y (en) * 2000-11-10 2001-09-05 昆明理工大学 Involute wildhaber-novikov gear
JP2005201295A (en) * 2004-01-13 2005-07-28 Mitsubishi Fuso Truck & Bus Corp Gear
US20060058151A1 (en) * 2004-09-13 2006-03-16 Illinois Tool Works, Inc. Zero degree operating pressure angle clearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105422795A (en) * 2015-11-17 2016-03-23 南京航空航天大学 Conical ring surface involute gear and machining method thereof
CN114987384A (en) * 2021-03-01 2022-09-02 株式会社东海理化电机制作所 Webbing retractor

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Granted publication date: 20100602

Termination date: 20120716