CN201013845Y - Full symmetry type three rings two-phase B grade decelerator - Google Patents
Full symmetry type three rings two-phase B grade decelerator Download PDFInfo
- Publication number
- CN201013845Y CN201013845Y CNU2007200346039U CN200720034603U CN201013845Y CN 201013845 Y CN201013845 Y CN 201013845Y CN U2007200346039 U CNU2007200346039 U CN U2007200346039U CN 200720034603 U CN200720034603 U CN 200720034603U CN 201013845 Y CN201013845 Y CN 201013845Y
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- internal tooth
- tooth ring
- ring plate
- high speed
- speed shaft
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Abstract
A completely symmetrical three-ring two-phase two stage gear reducer relates to the technical field of a crank shaft connection rod type internal tooth planetary transmission gear with small tooth number difference. At least two driven gears that are externally engaged with a driving gear are evenly and symmetrically arranged in the circumferential direction centered with the driving gear, and the driven gears are respectively, concentrically and fixedly connected with corresponding high-speed shafts; the two sides of a thick internal tooth ring plate in the box body are respectively provided with a thin internal tooth ring plate, and the two thin internal tooth ring plates are fixedly connected with each other; the thick internal tooth ring plates are respectively connected with the exterior of the high-speed shaft through a bearing and an eccentric sleeve; the two thin internal tooth ring plates are respectively connected with the exterior of the high-speed shaft through a bearing and an eccentric sleeve; the phase difference of the eccentric sleeve between the thick internal tooth ring plate and the high-speed shaft and the eccentric sleeve between the thin internal tooth ring plate and the high-speed shaft is 180 degrees; the exterior of an output shaft is fixedly connected with a central external gear which is engaged with the thick internal tooth ring plate and the thin internal tooth ring plate with a phase difference of 180 degrees. The utility model has no dead point, generates no impact load and can eliminate the impact and vibration of the whole machine.
Description
Technical field
The utility model relates to a kind of interior tooth planetary driving device technical field of few tooth difference of mechanical transmission power plant, particularly crank-linkage type.
Background technique
Advantage has obtained using widely few tooth difference internal tooth Gear Planet Transmission of crank-linkage type owing to having that velocity ratio is big, bearing capacity is strong, transmission efficiency is high and adaptability is strong etc.But be applied in the impact or the vibration problem of ubiquity fierceness under the high speed conditions.Guaranteeing under the retarder machining accuracy situation that the interior tooth planetary driving device existence of the few tooth difference of existing crank-linkage type impacts or the main cause of vibration has:
The centrifugal inertia force or the centrifugal inertia force square that produce when 1, retarder runs up can not get overall balance;
Producing amplitude when 2, each of retarder walked around the dead center position to the double-crank parallel-crank mechanism is infinitely-great impulsive load;
3, under mechanism's gravity and inertial force (square) effect, because the nonsymmetry of spatial structure, the support reaction of coaxial two side box bodies is asymmetric, and its amplitude is rotated and the alternation variation with input shaft.
At present, the interior tooth planetary driving device of few tooth difference of known crank-linkage type mainly contains few tooth difference internal tooth planetary reduction gear transmission device of monodentate ring, bidentate ring and three ring gear formulas.Chinese patent 00230087.6 discloses a kind of " double-crank bidentate ring flat-plate planetary speed reducer with small tooth number difference ", this retarder has adopted two phase differences to be mutually 180 ° double crank mechanism, the centrifugal inertia resultant force that can make two mechanisms is zero, but the centrifugal inertia force resultant moment of force between the mechanism is non-vanishing, under high speed conditions, the moment of inertia of this dynamic unbalance will make complete machine produce fierce the impact or vibration.Chinese patent discloses for No. 85106692 a kind of " three ring deceleration (or speedup) transmission devices ", this transmission device has adopted three phase differences to be mutually 120 ° double crank mechanism, the centrifugal inertia resultant force that three mechanisms produce is balance mutually, but centrifugal inertia force can not be for zero, so retarder can vibrate under high speed conditions equally in the synthetic moment of inertia of some direction.No. 92113625, Chinese patent disclosed " three-crankshaft formula little tooth difference speed reducer " is taked the high speed shaft that passes motion assembly center of gravity is carried out counterweight, reduces vibration to realize assembled machine balance; No. 97230101.1, Chinese patent disclosed " the complete dynamic balancing planetary driving device of engagement in the three-crankshaft ", having taked three phase differences is 0 °, 180 ° double crank mechanism, the quality of both sides mechanism homophase and its internal tooth ring plate (connecting rod) is half of intermediary agency's internal tooth ring plate (connecting rod) quality, so the inertial force and the moment of inertia of complete machine can obtain complete equilibrium, can make the vibration of retarder obtain certain inhibition, but owing to adopt the single shaft input to make three high speed shafts be in stressed asymmetrical state, the amplitude that produces when comprehensively double crank mechanism is crossed the dead point is infinitely-great impact.No. 00234570.6, Chinese patent disclosed " complete equilibrium, all carry vibration damping the two poles of the earth three-ring gear reducer ", the same inertial force and moment of inertia that can the balance complete machine with No. 97230101.1, Chinese patent, but existence because of the carrier gear driving mechanism, retarder is in the axial asymmetric layout of two high speed shafts, the amplitude that produces when making double crank mechanism cross undefined position is that infinitely-great impulsive load can not get balance, and act on the casing dynamic force by each rotating shaft two ends that mechanism produces and do not wait, thereby must cause retarder to produce vibration.
The model utility content
The purpose of this utility model is to overcome the deficiency that above-mentioned prior art exists, design a kind of impulsive load that do not produce when can the balance double crank mechanism crossing the dead center position, dynamic balanced controls centrifugal inertia force (square) again, thus the complete symmetric type three ring two-phase two stage reduction gears of complete machine shock and vibration can be eliminated.
The utility model input shaft, output shaft by bearings respectively on casing, concentric fixedly connected driving gear on input shaft, described input shaft and output shaft are arranged in parallel; Be characterized in: driving gear be the center circumferentially arrange at least two driven gears symmetrically, each driven gear respectively with the driving gear outer gearing; Respectively by the bearings high speed shaft identical with driven gear quantity, each high speed shaft and input shaft are arranged in parallel on casing, and each driven gear is fixedlyed connected with corresponding high speed shaft is concentric respectively; Also arrange a thick internal tooth ring plate in casing, arrange a thin internal tooth ring plate respectively in two sides of thick internal tooth ring plate, described thick internal tooth ring plate and two thin internal tooth ring plates are parallel to each other, and two thin internal tooth ring plates are affixed mutually; Offer the through hole identical with high speed shaft quantity on thick internal tooth ring plate, each through hole is connected to outside the high speed shaft by bearing and eccentric bushing; Offer the through hole identical with high speed shaft quantity on two thin internal tooth ring plates, each through hole is connected to outside the high speed shaft by bearing and eccentric bushing; The phase difference of the eccentric bushing between the eccentric bushing between thick internal tooth ring plate and the high speed shaft and thin internal tooth ring plate and the high speed shaft is 180 °; Affixed center external gear outside output shaft, described center external gear mesh with 180 ° phase difference with thick internal tooth ring plate, thin internal tooth ring plate respectively.
The utility model adopts the secondary transmission scheme.The straight toothed spur gear driving mechanism that first order transmission is made up of the driven gear of casing, input shaft and driving gear, 2 (or many) high speed shafts and equal number.Make each high speed shaft obtain the power input that equates by driven gear, driven gear can slow down or the constant speed transmission.Second level transmission comprises casing, high speed shaft, output shaft, and compositions such as eccentric bushing, thick, thin internal tooth ring plate, center external gear.First order transmission is carried out power and is evenly shunted, the input torque that makes each high speed shaft of second level transmission obtain equating, through the multicrank linkage mechanism that high speed shaft, eccentric bushing and thick, thin internal tooth ring plate constitute, thick by it, thin internal gear is finished the deceleration of output shaft and is exported with few tooth difference engagement of center external gear.
It is zero that the utility model can make the complete machine centrifugal inertia force rationally reach centrifugal inertia resultant force square, reaches purpose quiet, transient equiliblium, eliminates retarder and changes the vibration problem that produces because of inertial load.The utility model does not have the dead point, does not produce impulsive load, dynamic balanced controls centrifugal inertia force (square) again, thus can eliminate the complete machine shock and vibration.
All bearings between thick internal tooth ring plate of the present utility model and thick internal tooth ring plate and the high speed shaft and total quality of eccentric bushing equal total quality of the parts of all eccentric bushings between two thin internal tooth ring plates and two thin internal tooth ring plates and the high speed shaft and bearing and affixed two thin internal tooth ring plates.Its objective is for equilibrium centrifugation inertial force and centrifugal inertia force square.
Produce for convenience, the quality of two thin internal tooth ring plates of the present utility model equates.
In addition, between two thin internal tooth ring plates annular ring is set, the periphery of two thin internal tooth ring plates is fixedlyed connected with annular ring respectively.
Description of drawings
Fig. 1 is an end view drawing of the present utility model;
Fig. 2 is an A-A cut-away view among Fig. 1.
The tool present embodiment
As shown in Figure 1, 2, on casing 11 respectively by bearings input shaft 14, output shaft 18, three high speed shafts 3,4,5, each layout that is parallel to each other.
Concentric fixedly connected driving gear 2 on input shaft 14, the concentric fixedly connected driven gear 1,12,6 of difference on high speed shaft 3,4,5.And, three driven gears 1,12,6 be arranged symmetrically in driving gear 2 be the center week upwards, three driven gears 1,12,6 respectively with driving gear 2 outer gearings.
In casing 11, also arrange a thick internal tooth ring plate 17, arrange thin internal tooth ring plate 16,22 respectively in two sides of thick internal tooth ring plate 17, thick internal tooth ring plate 17 and two thin internal tooth ring plates 16,22 are parallel to each other, the periphery that 8, two thin internal tooth ring plates 16,22 of annular ring are set between two thin internal tooth ring plates 16,22 is fixedlyed connected with annular ring 8 by screw 7 respectively.
On thick internal tooth ring plate 17, offer three through holes, on two thin internal tooth ring plates 16,22, also offer three through holes respectively, three high speed shafts 3,4,5 are set in respectively in each through hole.Put eccentric bushing 10 at high speed shaft 3 peripheral hardwares, between a through hole of eccentric bushing 10 and thick internal tooth ring plate 17, bearing 9 is set; Setting also is provided with eccentric bushing 15,21 outside high speed shaft 3, between the through hole of eccentric bushing 15 and thin internal tooth ring plate 22 bearing 20 is set, and between this through hole of eccentric bushing 21 and thin internal tooth ring plate 16 bearing 13 is set.The quality of two eccentric bushings 15,13 is equal,
The quality of two thin internal tooth ring plates 16,22 equates, and total quality of all bearings between thick internal tooth ring plate 17 and thick internal tooth ring plate 17 and the high speed shaft 3,4,5 and eccentric bushing equals all eccentric bushings between 16,22 and two thin internal tooth ring plates 16,22 of two thin internal tooth ring plates and the high speed shaft 3,4,5 and the annular ring 8 of bearing and affixed two thin internal tooth ring plates 16,22, total quality of screw 7.
Two eccentric bushings 15,13 have same phase, and the phase difference of eccentric bushing 15,13 and eccentric bushing 10 is 180 °.
Between other two through holes, each eccentric bushing and bearing are set equally, respectively between other two through holes of high speed shaft 4,5 and thick internal tooth ring plate 17, at 4,5 and two thin internal tooth ring plates 16,22 of high speed shaft.
Affixed center external gear 19 outside output shaft 18, center external gear 19 mesh in the tooth difference with 180 ° phase place less with thick internal tooth ring plate 17, thin internal tooth ring plate 16,22 respectively.
The purpose of first order transmission of the present utility model is that the input load that acts on each high speed shaft of connecting rod planet internal tooth engagement transmission mechanism of the second level is equal fully, eliminates the dead point of mechanism and the shock problem of generation thereof thus through after the shunting of first order transmission symmetry.According to theory analysis as can be known, phase difference 180 ° two-phase mechanism each other satisfies aforementioned complete symmetry input and two cover planet internal gears equate under the situation with the engaging force of center external gear, when connecting rod is crossed the dead point, the infinitely great impulsive load that each tooth plate acts on the axle will be able to the balance elimination.
By three connecting rod planet internal tooth ring plates that thick internal tooth ring plate and two thin internal tooth ring plates and each eccentric bushing, bearing are formed, be the connecting rod of plane connecting rod, be again the planet internal gear of engagement Gear Planet Transmission in few tooth difference.Two thin internal tooth ring plates are arranged in the both sides of thick internal tooth ring plate fully symmetrically, and form the link that is fixed as one.She Ji purpose is like this: 1. the engagement of maintenance integrated in the course of the work thin internal tooth ring plate of retarder and center external gear makes a concerted effort to equal the engaging force of thick internal gear and center external gear, and the two direction is opposite; 2. the radial force that the planet tooth plate is acted on high speed shaft and the output shaft is symmetrically distributed vertically as far as possible, reduce with axle box two-side supporting bearing radially the difference of counter-force with the variation of corner; 3. reduce the static indeterminacy number of times of complete machine, make theory analysis research reliable more, convenient.
Two-phase driving mechanism corresponding motion component quality and gross mass equate, and keep 180 ° phase difference on the space, can make the complete machine centrifugal inertia force rationally reach centrifugal inertia resultant force square is zero, reaches purpose quiet, transient equiliblium, eliminates retarder and changes the vibration problem that produces because of inertial load.
Claims (4)
1. complete symmetric type three ring two-phase two stage reduction gears comprise casing, input shaft, the output shaft by bearings respectively on casing, and concentric fixedly connected driving gear on input shaft, described input shaft and output shaft are arranged in parallel; It is characterized in that: driving gear be the center circumferentially arrange at least two driven gears symmetrically, each driven gear respectively with the driving gear outer gearing; Respectively by the bearings high speed shaft identical with driven gear quantity, each high speed shaft and input shaft are arranged in parallel on casing, and each driven gear is fixedlyed connected with corresponding high speed shaft is concentric respectively; Also arrange a thick internal tooth ring plate in casing, arrange a thin internal tooth ring plate respectively in two sides of thick internal tooth ring plate, described thick internal tooth ring plate and two thin internal tooth ring plates are parallel to each other, and two thin internal tooth ring plates are affixed mutually; Offer the through hole identical with high speed shaft quantity on thick internal tooth ring plate, each through hole is connected to outside the high speed shaft by bearing and eccentric bushing; Offer the through hole identical with high speed shaft quantity on two thin internal tooth ring plates, each through hole is connected to outside the high speed shaft by bearing and eccentric bushing; The phase difference of the eccentric bushing between the eccentric bushing between thick internal tooth ring plate and the high speed shaft and thin internal tooth ring plate and the high speed shaft is 180 °; Affixed center external gear outside output shaft, described center external gear mesh with 180 ° phase difference with thick internal tooth ring plate, thin internal tooth ring plate respectively.
2. according to the described complete symmetric type three ring two-phase two stage reduction gears of claim 1, it is characterized in that: all bearings between thick internal tooth ring plate and thick internal tooth ring plate and the high speed shaft and total quality of eccentric bushing equal total quality of the parts of all eccentric bushings between two thin internal tooth ring plates and two thin internal tooth ring plates and the high speed shaft and bearing and affixed two thin internal tooth ring plates.
3. according to the described complete symmetric type three ring two-phase two stage reduction gears of claim 1, it is characterized in that: the quality of two thin internal tooth ring plates equates.
4. according to claim 1 or 2 or 3 described complete symmetric type three ring two-phase two stage reduction gears, it is characterized in that: between two thin internal tooth ring plates annular ring is set, the periphery of two thin internal tooth ring plates is fixedlyed connected with annular ring respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200346039U CN201013845Y (en) | 2007-02-09 | 2007-02-09 | Full symmetry type three rings two-phase B grade decelerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200346039U CN201013845Y (en) | 2007-02-09 | 2007-02-09 | Full symmetry type three rings two-phase B grade decelerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201013845Y true CN201013845Y (en) | 2008-01-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007200346039U Expired - Fee Related CN201013845Y (en) | 2007-02-09 | 2007-02-09 | Full symmetry type three rings two-phase B grade decelerator |
Country Status (1)
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| CN (1) | CN201013845Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102116364A (en) * | 2011-01-19 | 2011-07-06 | 南京高精齿轮集团有限公司 | Combined speed reducer for plate-rolling machine |
| CN106704493A (en) * | 2017-01-24 | 2017-05-24 | 陕西理工学院 | Tricyclic speed reducer capable of balancing inertia moment of annular plates |
| CN108082464A (en) * | 2016-11-21 | 2018-05-29 | 瑞士玛瑞恩克直升机公司 | Lifting airscrew speed changer |
-
2007
- 2007-02-09 CN CNU2007200346039U patent/CN201013845Y/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102116364A (en) * | 2011-01-19 | 2011-07-06 | 南京高精齿轮集团有限公司 | Combined speed reducer for plate-rolling machine |
| CN102116364B (en) * | 2011-01-19 | 2014-02-19 | 南京高精齿轮集团有限公司 | Combined speed reducer for plate-rolling machine |
| CN108082464A (en) * | 2016-11-21 | 2018-05-29 | 瑞士玛瑞恩克直升机公司 | Lifting airscrew speed changer |
| CN106704493A (en) * | 2017-01-24 | 2017-05-24 | 陕西理工学院 | Tricyclic speed reducer capable of balancing inertia moment of annular plates |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080130 Termination date: 20110209 |