CN109185396A - Bilateral drives fewer differential teeth planetary conic reducer - Google Patents
Bilateral drives fewer differential teeth planetary conic reducer Download PDFInfo
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- CN109185396A CN109185396A CN201811295136.4A CN201811295136A CN109185396A CN 109185396 A CN109185396 A CN 109185396A CN 201811295136 A CN201811295136 A CN 201811295136A CN 109185396 A CN109185396 A CN 109185396A
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- Prior art keywords
- gear
- teeth
- difference
- bevel gear
- degree
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Classifications
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2854—Toothed gearings for conveying rotary motion with gears having orbital motion involving conical gears
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention discloses a kind of bilaterals to drive fewer differential teeth planetary conic reducer, comprising: two groups of few teeth difference bevel gears, zero teeth difference type output mechanism, cross connecting structure.Wherein two groups of few teeth difference bevel gears are supplied to output gear bilateral driving force.Output mechanism two groups of teeth tooth number is identical, therefore can connect firmly.Advantage there are two connecting firmly, to improve output torque, reduces bearing burden first is that eliminating the driving force of part with internal force balance.Second is that retarder number of bearings is fallen below 6, simplify structure.The invention avoids the heavy dutys of bearing, are undertaken by gear engagement, solve the problems, such as that bearing is easily damaged, improve carrying and the service life of retarder；Because retarder efficiency of the present invention is higher and output torque is larger, it is suitable for middle low-speed heave-load high-torque and exports situation；Together, the requirement that each autokinesis that do not interfere is connected with certain bonding strength rigidity is realized by two, three tie point interconnections in each corresponding part of output mechanism.
Description
Technical field
The invention belongs to mechanical engineering technical fields, and in particular to bilateral driving fewer differential teeth planetary conic reducer or
The nutating gear gearing speed-reducer of bilateral driving.
Background technique
Plane internal messing less teeth difference transmission has many advantages, such as that contact strength is high, torque is big, wide by high performance retarder institute
General use.For example, RV retarder, internal parallel moving gears reducer, three-ring speed reducer etc..However, with the increase of output torque,
What is gone wrong first is bearing, because bearing working is in high revolving speed, simultaneously because heavily loaded, radial force is very big, long-term heavy load
Work, it is easy to go wrong.Paper both domestic and external has common recognition to this, i.e. bearing is to improve these types of gear reduction unit performance
Bottleneck.The plane less teeth difference transmission problem larger there are one pressure angle, such as the angle of engagement of a tooth difference internal messing are generally
54-56 degree.The angle of engagement of two teeth difference internal messing is also up to 40-42 degree, therefore the stress condition of gear is undesirable.
And Bevel Gear Transmission belongs to spherical mechanism, spherical mechanism is the popularization of plane mechanism, and plane mechanism is spherical mechanism
Special circumstances, it is believed that plane mechanism is the sub-fraction in the spherical surface of radius infinity.So in the model of spherical mechanism
Enclose it is interior studied, theoretically also include plane mechanism, mechanism can be optimized in a wider context.
Meat and potatoes is RV gear in RV (rotating vector) gear reduction unit, i.e. rotating vector gear, actually
It is planetary gear, for planetary gear itself in addition to rotation, center is still around the revolution of RV gear reduction unit center.One RV gear by
Power is illustrated in fig. 1 shown below, it will be seen from figure 1 that bearing is more taller than load force.General RV gear reduction unit have to
Few two RV gears, it is symmetrical in 180 degree, and driven with two or three crankshafts.Input and output principle such as Fig. 2 of RV gear
It is shown, wherein the rotation of crankshaft drives the revolution of RV gear 1 and RV gear 2, the rotation of RV gear 2 is by being as revolution input
Bar rotation output, the internal gear that RV gear is fixed on internal gear rack with one engage.It can be seen that the output torque of tie-rod is
What several bearings by being fixed on tie-rod provided, bearing is capable of providing great radial force, tie-rod can correspond to obtain it is great
Output torque.Because having relative translational movement between two RV gears, cannot be connected therebetween, i.e., each RV gear is at least
Will there are two bearings to drive, and bearing stress is larger, and high speed rotation, thus causes workload weight, easy to damage.From figure
2 it can also be seen that two RV gears of driving at least want 8 bearings, and along with input and output, more than ten of bearing is always needed.
Nutating gear transmission is as a kind of novel transmission device, relative to traditional Worm Wheel System and roller gear
For transmission, have the advantages that many incomparable, big including transmission ratio, registration is high, stable drive, structure are tight
It gathers, efficiency and reliability height etc..Meanwhile some such as internal bevel gear processing difficulties are also faced at present and internal-external gear engagement is dry
Relate to and can only unilateral driving etc. need the problem of further studying and exploring.
Summary of the invention
Aiming at the problems existing in the prior art, the present invention provides a kind of few teeth difference and zero differential teeth planetary bevel gear is slowed down
Plane few teeth difference internal-external gear engaged transmission in RV retarder is changed to spherical surface few teeth difference internal-external gear by device, the retarder
Engaged transmission, i.e., rise to spherical surface by plane, the bearing in RV retarder, connected between two RV gears can be cancelled, directly
It connects the two RV gears or is connected firmly for planetary gear, avoid influence of the bearing to retarder performance.In order to improve nutating
In gear drive, it can only be also added inside and outside zero tooth difference other than two planetary gears are connected firmly unilateral the problem of driving
Bevel gear engagement, the spinning motion in planetary gear is exported.On this basis, and cross connecting structure is devised, used
To connect corresponding part and input and output component in two groups of nutating gears.After these measures, retarder may be implemented
Bilateral driving, be driven in heavy duty only undertaken by few teeth difference and zero tooth difference meshed gears.
The present invention has the advantages that
(1) bevel gear engages inside and outside few teeth difference, has the advantages that contact stress is small, driving force is big.
(2) it is driven using bilateral, increases bevel gear engagement inside and outside zero tooth difference, output torque is big, reduces the negative of bearing
It carries.
(3) compared with RV retarder, number of components used in the retarder is few, and structure is simple, and assembly is easy.
Detailed description of the invention
Fig. 1 is a RV strength of gear schematic diagram in the prior art.
Fig. 2 is the input and output schematic illustration of RV gear in the prior art.
Fig. 3 is by two RV gears in the present invention as the schematic diagram that is connected after bevel gear.
Fig. 4 is inside and outside bevel gear mesh schematic representation, wherein outer bevel gear is RV gear.
Fig. 5 is zero tooth difference Bevel Gear Transmission schematic illustration.
Fig. 6 is zero tooth difference bevel gear displacement design diagram.
Fig. 7 is that bilateral drives zero tooth difference mesh schematic representation.
Fig. 8 is bilateral driving bevel gear few teeth difference and zero tooth difference part body schematic diagram.
Fig. 9 is fixed shaft gear train revolving speed schematic diagram.
Figure 10 is the first mechanism that the outer bevel gear of few teeth difference is rack.
Figure 11 is second of mechanism that the outer bevel gear of zero tooth difference is rack.
Figure 12 is the third mechanism that few teeth difference internal bevel gear is rack.
Figure 13 is the 4th kind of mechanism that zero tooth difference internal bevel gear is rack.
Figure 14 is the schematic diagram that cross connecting structure uses three point attachment scheme.
Figure 15 is the schematic diagram that cross connecting structure uses two o'clock connection scheme.
Figure 16 is the overall structure diagram that the present invention uses the first mechanism.
Specific embodiment
Below in conjunction with drawings and examples, the present invention is described in further detail.
The present invention provides a kind of bilateral driving fewer differential teeth planetary conic reducer, is bored by two pairs of few teeth differences being arranged symmetrically
Gear and output mechanism and cross connecting structure composition；Each pair of intermeshing few teeth difference bevel gear all includes that a number of teeth is more
Gear wheel and the few pinion gear of a number of teeth, the teeth number difference of gear wheel and pinion gear is 1-4, and the number of teeth relative to gear is very
It is few, belong to less teeth difference transmission；The conical point of two pairs of bevel gears is overlapped；Two gear wheels are parallel to each other, and connect firmly together, are located at
Conical point two sides, are mutually 180 degree；Two pinion gears are also parallel to each other, and connect firmly together, are located at conical point two sides, are mutually 180
Degree.
Wherein pinion gear is fixed with rack, and gear wheel is mounted on a sloping shaft by bearing, and sloping shaft passes through a pair
Bearing is connect with rack, as high speed input terminal；Gear wheel participates in two and rotates, a rotation on sloping shaft, another
It revolves together with sloping shaft；Gear wheel also passes through an output mechanism output rotation.
Output mechanism is realized using the bevel gear engaged transmission of two pair of zero tooth difference, to export the rotation of gear wheel；It is each pair of
Zero-tooth difference gear includes the identical gear of two numbers of teeth, one of them connects firmly with gear wheel or is extended by the tooth of gear wheel,
Another is equipped with bearing between rack, and output slowly runs.
Cross connecting structure is corresponding part in the gear two pair of zero tooth difference, i.e., corresponding two output gears, phase
Mutually linked together by 120 degree of 3 points be distributed；Corresponding another pair gear passes through 3 points and upper and lower two of 120 degree of distributions
A bearing is connected；This 6 arranged crosswises differ 60 degree.
Cross connecting structure is corresponding part in the gear two pair of zero tooth difference；I.e. corresponding two output gears, phase
It is mutually linked together by the two o'clock that 180 degree is distributed, and each point has certain width；It is corresponding another pair of by 180
Two points of degree distribution are connected with upper and lower two bearings；This 4 arranged crosswises differ 90 degree.
The big pinion gear of few teeth difference bevel gear can exchange, that is, gear wheel is fixed with rack, and pinion gear is installed by bearing
On sloping shaft.
Output mechanism and rack can exchange.The big pinion gear of few teeth difference bevel gear can exchange, while output and rack
It can exchange therewith.The bevel gear is straight bevel gear, helical bevel gear or spiral bevel gear.
Based on multiple bearing problem existing in the prior art, the present invention provides a kind of bilateral driving fewer differential teeth planetaries to bore tooth
Wheel decelerator, on the basis of structure shown in Fig. 2, two RV gears are rotated to an angle counterclockwise, and (generally higher than 0 is less than
45 degree), and RV gear is all processed into outer cone tooth, then the mutual translation between two RV gears disappears immediately, then can be with
Two gears with outer vertebra tooth are connected, one group of outer bevel gear in the present invention is formed.This reduces the numbers of bearing
Amount, such as Fig. 3.
Due to using outer bevel gear, concrete form such as Fig. 4, input revolution is engaged with internal bevel gear；But meanwhile exporting machine
Structure is without therefore, invention increases other two pairs of zero-tooth difference gears engaged transmissions to be used as output mechanism.That is two number of teeth phases
Deng bevel gear engagement.The engagement of zero tooth difference should use two identical gears of shape in the ideal situation, such as Fig. 5 institute
Show, working pitch point is located at P.
But since it is desired that two sides are involved in engagement and export, therefore a pair of of zero-tooth difference gear can only occupy a side position,
Other side position is reserved to a pair of of gear on opposite.So the gear of two pair of zero tooth difference must carry out displacement design.Every side tooth
The occupied position of wheel must be as shown in fig. 6, the gear of a pair of zero tooth difference only occupies upper half side position in i.e. Fig. 6.But according to
Its working pitch point position of theory analysis, the P point still in figure are identical as theory state.Working pitch point is fallen on spherical surface in other words
Other than gear, in fact, stress point passes through node P.
According to centrosymmetric principle, using ball center as symmetrical centre, the meshing gear of other side, then, two are arranged
It is as shown in Figure 7 to zero tooth difference meshing gear.
Few teeth difference is engaged with zero tooth difference again and is connected, powerdriven major part is constituted.Specific connection method
There are two types of, the first is: the outer bevel gear of zero tooth difference and few teeth difference being connected firmly or be simply made into a part, zero tooth is poor
It is used as rack with internal bevel gear one of few teeth difference, another is as output.Second is: two internal bevel gears are connected firmly or done
At a part, outer bevel gear one is used as rack, another is as output.The power drive mechanism that two kinds of connection methods obtain
According to centrosymmetric principle, 180 degree is differed, positioned at the two sides of ball center.The schematic diagram of the part body is as shown in Figure 8.
By the analysis of rational mechanics it is recognised that the engagement force of few teeth difference and zero-tooth difference gear is bigger, and driving force
It is then smaller.Driving force works in fast state, so, mechanism of the present invention completely avoids the heavy duty work of bearing, heavy burden
It carries work to be undertaken by gear engagement completely, this just fundamentally solves the problems, such as that bearing is easily damaged.
The conversion of mechanism
In fact, planet few teeth difference engaged transmission is developed from fixed shaft gear train, fixed shaft gear train is as shown in figure 9, gear 1
With gear 2 in P point gearing, 1 direction of rotation of gear is V1, and size is2 direction of rotation of gear is V2, and size isGear
1 is external gear, and diameter is smaller than gear 2, and the number of teeth is few, and revolving speed is high, that is,As soon as entire mechanism superposition is rotated,
As planetary gear train.It is rotated according in the direction V1 or the direction V2 superposition, what it is there are also superposition isOrAccording to arrangement
Combination, can have 4 kinds of situations, respectively obtain 4 kinds of mechanisms.
The first mechanism, as shown in Figure 10, in the direction V1 superpositionThen 1 revolving speed of gear,Gear 1 is rack, and gear 2 participates in two rotations, revolution and rotation.Revolution is input, rotation
It is driven and is exported by zero tooth difference.
Second of mechanism, as shown in figure 11, in the direction V1 superpositionThen gear 1 is pure rotation, revolving speedAs output, gear 2 only revolves, and without rotation, can be arrived by a zero tooth difference transmission connection
Rack.Actually this mechanism only swaps round the rack of the 1st kind of mechanism with output.
The third mechanism, as shown in figure 12, in the direction V2 superpositionThen 2 revolving speed of gear,Gear 2 is rack, and gear 1 participates in two rotations, revolution and rotation.Revolution is input, rotation
It is exported by zero-tooth-difference mechanism.
4th kind of mechanism, as shown in figure 13, in the direction V2 superpositionThen gear 2 is pure rotation, revolving speedAs output, gear 1 only revolves, and without rotation, can be arrived by a zero tooth difference transmission connection
Rack.Actually this mechanism only swaps round the rack of the 3rd kind of mechanism with output.
Cross connecting structure
Cross connecting structure be the corresponding part of two set of zero tooth difference transmission gear is connected, and respectively with external connection
Output movement.Even if there is certain relative motion between them, and do not interfere, and its connection should also have certain intensity
And rigidity.The present invention provides the two schemes of cross connecting structure,
The first, three point attachment scheme；
As shown in figure 14, gear and gear, gear are connect with outside by 3 points, and two groups of teeth wheel shape is at interconnection, and two groups
Corresponding gear 1 in gear is connected with each other by 3 points of 120 degree of distributions of difference, then is connect with output par, c.Gear 2
By being connect at 120 degree of 3 points be distributed with two bearings after interconnection.3 of 3 points of connection gear 1 and connection gear 2
60 degree of point difference, is inserted into mutually the neutral gear of other side.
Second, two o'clock connection scheme；
As shown in figure 15, gear and gear, gear are connect with outside by two o'clock, and two points will have certain width, with
Torque is transmitted, and there are certain strength and stiffness, for two groups of teeth wheel shape at interconnection, connection method is as follows:
Corresponding gear 1 in two groups of teeth wheel is mutual by two with the one fixed width point of difference 180 degree distribution
Connection, then connect with output par, c.Pass through two with the one fixed width point minute in 180 degree distribution after the interconnection of gear 2
It is not connect with two bearings, two points of connection gear 1 differ 90 degree with two points of connection gear 2, are inserted into other side's mutually
Neutral gear.
One scheme of the first mechanism specific implementation, as shown in figure 16.
Claims (9)
1. a kind of bilateral drives fewer differential teeth planetary conic reducer, the few teeth difference bevel gear being arranged symmetrically by two Duis and output
Mechanism and cross connecting structure composition；Each pair of intermeshing few teeth difference bevel gear all includes the gear wheel and one more than a number of teeth
The teeth number difference of the few pinion gear of a number of teeth, big pinion gear is 1-4, and the number of teeth relative to gear is seldom, belongs to less teeth difference transmission；Two
The conical point of bevel gear is overlapped；Two gear wheels are parallel to each other, and connect firmly together, are located at conical point two sides, are mutually 180
Degree；Two pinion gears are also parallel to each other, and connect firmly together, are located at conical point two sides, are mutually 180 degree.
2. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, wherein pinion gear and rack
Fixed, gear wheel is mounted on a sloping shaft by bearing, and sloping shaft is connect by a pair of bearings with rack, defeated as high speed
Enter end；Gear wheel participates in two rotations, and a rotation on sloping shaft, another revolves together with sloping shaft；Gear wheel is also
Rotation is exported by an output mechanism.
3. a kind of bilateral according to claim 1 or 2 drives fewer differential teeth planetary conic reducer, it is characterised in that: defeated
Mechanism is realized using the bevel gear engaged transmission of two pair of zero tooth difference out, to export the rotation of gear wheel；Each pair of zero-tooth difference gear
Including the identical gear of two numbers of teeth, one of them connects firmly with gear wheel or is extended by the tooth of gear wheel, another with
Bearing is equipped between rack, output slowly runs.
4. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, it is characterised in that: intersect
Connection structure is corresponding part in the gear two pair of zero tooth difference, i.e., corresponding two output gears, each other by 120 degree points
3 points of cloth link together；Corresponding another pair gear is connected by 3 points of 120 degree of distributions with upper and lower two bearings；This
6 arranged crosswises differ 60 degree.
5. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, it is characterised in that: intersect
Connection structure is corresponding part in the gear two pair of zero tooth difference；I.e. corresponding two output gears, each other by 180 degree point
The two o'clock of cloth links together, and each point has certain width；Corresponding another pair of two points being distributed by 180 degree
It is connected with upper and lower two bearings；This 4 arranged crosswises differ 90 degree.
6. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, it is characterised in that: few tooth
The big pinion gear of poor bevel gear can exchange, that is, gear wheel is fixed with rack, and pinion gear is mounted on sloping shaft by bearing.
7. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, it is characterised in that: output
Mechanism and rack can exchange.
8. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, it is characterised in that: few tooth
The big pinion gear of poor bevel gear can exchange, while output and rack can exchange therewith.
9. a kind of bilateral according to claim 1 drives fewer differential teeth planetary conic reducer, it is characterised in that: described
Bevel gear be straight bevel gear, helical bevel gear or spiral bevel gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811295136.4A CN109185396B (en) | 2018-11-01 | 2018-11-01 | Double-side driving planetary bevel gear reducer with small tooth difference |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811295136.4A CN109185396B (en) | 2018-11-01 | 2018-11-01 | Double-side driving planetary bevel gear reducer with small tooth difference |
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| Publication Number | Publication Date |
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| CN109185396A true CN109185396A (en) | 2019-01-11 |
| CN109185396B CN109185396B (en) | 2020-09-25 |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6091045A (en) * | 1983-10-24 | 1985-05-22 | Sanwa Tekki Corp | Face gear device |
| CN2059949U (en) * | 1989-09-09 | 1990-08-01 | 曹金甲 | Bevel gear waveguide speed reducer |
| JPH04191546A (en) * | 1990-11-27 | 1992-07-09 | Takaoka Electric Mfg Co Ltd | Speed reduction device |
| CN2161595Y (en) * | 1993-03-12 | 1994-04-13 | 南京理工大学 | Integrated hoist |
| DE102011078130A1 (en) * | 2011-06-27 | 2012-12-27 | Zf Friedrichshafen Ag | Epicyclic gear has two eccentric wheels with beveloid teeth, which are mesh-engaged with cylindrical gears of ring gears, and eccentric shafts which are inclined relative to central shaft |
| CN103912637A (en) * | 2014-04-28 | 2014-07-09 | 江苏泰隆减速机股份有限公司 | Special vertical star wheel reducer for ladle turret |
| CN106246812A (en) * | 2016-09-19 | 2016-12-21 | 福州大学 | Bilateral twin-stage internal messing bi-arc bevel gear nutation reducer and method of work |
| CN107514443A (en) * | 2017-07-25 | 2017-12-26 | 罗灿 | Single denominator subtractive decelerator |
-
2018
- 2018-11-01 CN CN201811295136.4A patent/CN109185396B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6091045A (en) * | 1983-10-24 | 1985-05-22 | Sanwa Tekki Corp | Face gear device |
| CN2059949U (en) * | 1989-09-09 | 1990-08-01 | 曹金甲 | Bevel gear waveguide speed reducer |
| JPH04191546A (en) * | 1990-11-27 | 1992-07-09 | Takaoka Electric Mfg Co Ltd | Speed reduction device |
| CN2161595Y (en) * | 1993-03-12 | 1994-04-13 | 南京理工大学 | Integrated hoist |
| DE102011078130A1 (en) * | 2011-06-27 | 2012-12-27 | Zf Friedrichshafen Ag | Epicyclic gear has two eccentric wheels with beveloid teeth, which are mesh-engaged with cylindrical gears of ring gears, and eccentric shafts which are inclined relative to central shaft |
| CN103912637A (en) * | 2014-04-28 | 2014-07-09 | 江苏泰隆减速机股份有限公司 | Special vertical star wheel reducer for ladle turret |
| CN106246812A (en) * | 2016-09-19 | 2016-12-21 | 福州大学 | Bilateral twin-stage internal messing bi-arc bevel gear nutation reducer and method of work |
| CN107514443A (en) * | 2017-07-25 | 2017-12-26 | 罗灿 | Single denominator subtractive decelerator |
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| Publication number | Publication date |
|---|---|
| CN109185396B (en) | 2020-09-25 |
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