CN201032823Y - Tea machine transmission device with varied transmission ratio - Google Patents
Tea machine transmission device with varied transmission ratio Download PDFInfo
- Publication number
- CN201032823Y CN201032823Y CNU200720152739XU CN200720152739U CN201032823Y CN 201032823 Y CN201032823 Y CN 201032823Y CN U200720152739X U CNU200720152739X U CN U200720152739XU CN 200720152739 U CN200720152739 U CN 200720152739U CN 201032823 Y CN201032823 Y CN 201032823Y
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- tea
- circular gear
- circular
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Abstract
The utility model relates to a tea machine variable transmission ratio drive device; the tea machine variable transmission ratio drive device between a tea machine shaft and a speed reducer is provided with a group of non-circular gear drive mechanism. The pitch curve of mutually engaged gears of the non-circular gear mechanism is determined by the non-circular gear pair transmission ratio function given according to the motion law of the tea machine shaft and the gear center distance. The non-circular gear mechanism commonly uses the elliptic gear, and also can use other types of non-circular gears according to the drive requirements. The device can realize the variable transmission ratio drive to make a frying tool implement the non-uniform angular velocity rotation; the instantaneous angular velocity changes according to a certain law in order to meet the requirements of tea making process, improve the tea quality and simultaneously reduce the load fluctuation range of a motor and a drive system. The utility model can be used in a long plate type flat tea frying machine, and also can be used in other tea making machines having similar requirements.
Description
Technical field
The utility model relates to tealeaves frying machinery, particularly tea machine transmission device.
Background technology
The transmission device of long slab formula Tea Frying Device tool is made up of transmission parts such as decelerator, clutch and band transmission, chain transmission, gear drives.In order to adapt to the bright leaf of different conditions and each stage of tealeaves frying needs to tea arbor different rotating speeds, some tea machine also is provided with mechanical variable-speed unit or adopts electromagnetic adjustable speed motor or frequency converter timing.But the transmission device of present existing long slab formula Tea Frying Device tool, its essence all belongs to the stable drive ratio transmission, and motor rotates the stir-fry tool that drives on tea arbor and the axle through transmission device and do the uniform angular velocity rotation by the rotating speed of setting up in frying pan.
Long slab formula Tea Frying Device is fried plate and is circled, and in fact fries tool and frying pan, tealeaves friction, and to tea carding, flattening, polishing, the effective frying scope that plays the frying effect approximately has only the garden cambered surface of about 90 ° of frying pan pot bottoms.The stir-fry tool is finished a frying tealeaves action back and is turned over above frying pan, and returning effective frying scope starting point is the idle stroke of returning.According to the requirement of tea-manufacturing technology, in effective frying angle, rotating speed should hang down, and suitably sulks are beneficial to tealeaves and manage straight slivering, flatten shaping.For this reason, once some tea machine was provided with sensor on main shaft, and frying cuts off the power supply when tool forwards in effective frying angular range shuts down the some time, and then starter motor, but the method all has very big infringement to electrical equipment and mechanical part.In effective frying angle, fry tool and be subjected to very big resistance on the other hand, the idle stroke beyond this is near zero load, and the load and the power swing of motor and transmission system are big.So no matter from the requirement of tealeaves stir-frying-technology, still from reducing the angle of load of tea machine and power swing, requiring tea machine main shaft to make non-uniform angular velocity rotates, angular speed is little in the time of in effective frying angular range, rotate slow, to satisfy the tea-manufacturing technology needs, can reduce the load of power and transmission system again; Big at idle stroke angular speed, rotate soon, fry moving number of times to guarantee the tealeaves unit interval, enhance productivity.Therefore need a kind ofly can be converted into the variable ratio transmission device that non-uniform angular velocity rotates, instantaneous angular velocity changes according to certain rules of tea arbor to the uniform rotation of motor by decelerator output.
Summary of the invention
In order to overcome existing tea machine transmission device, can not need realize that the non-uniform angular velocity of tea machine main shaft rotates by stir-frying-technology, and motor and the big deficiency of the transmission mechanism fluctuation of load, the utility model provides a kind of variable ratio transmission device, this device can be realized the variable ratio transmission, this device gearratio changes by a certain definite rule, make fry tool tea machine main shaft instantaneous angular velocity when effective frying angular range little, rotate slow, idle stroke angular speed is big, satisfy the tea making needs better, reduce the fluctuation of load, needed instantaneous peak power when reducing the work of tea machine.The utility model can be used for long slab formula Tea Frying Device, also can be used to have other tea manufacturing machines of similar demand.
The technical scheme that its technical problem that solves the utility model adopts is: the non-circular gear transmission mechanism is set on the driving-chain between tea arbor and the decelerator.The pitch curve of the gear that its non-circular gear mechanism is engaged with each other is determined by noncircular gear pair transmission ratio function given by the tea arbor characteristics of motion and two gear centres distance.The connected mode of the driven gear of non-circular gear mechanism and tea arbor turns over all gearratio period of change numbers by driven gear and decides, when gearratio changes one-period, driven gear can be directly installed on the tea arbor, also can drive the tea arbor indirectly by 1: 1 stable drive ratio gear drive of gearratio or chain transmission; When gearratio changes n cycle (n be 2,3 etc. integer), driven gear passes through gearratio i
12=1: stable drive ratio gear drive or the chain transmission of n drive the tea arbor indirectly.
Non-circular gear mechanism can be the gear mechanism of forming with two numbers of teeth and the elliptic gear that modulus equates, eccentric ratio e is identical.
Non-circular gear mechanism can be the gear mechanism of forming with two deformed elliptic gears.
Non-circular gear mechanism can be with two non-circles--the gear mechanism that circular gear is formed, the pitch curve of non-circle--circular gear is made up of arc section and the smooth connection of non-circular curve section.
Non-circular gear mechanism can be the gear mechanism of forming with eccentric gear and conjugation non-circular gear.
Non-circular gear mechanism can also be the gear mechanism of forming with elliptic gear and deformed elliptic gear.
Non-circular gear mechanism can also be the gear mechanism of forming with oval gear
Non-circular gear mechanism can also be the non-circular gear fixed shaft gear train.
Motor drives the uniform rotation of non-circular gear mechanism driving gear through decelerator, transmission parts, clutch, non-circular gear mechanism driven gear, tea arbor, stir-fry tool are made non-uniform angular velocity according to certain rules and are rotated, satisfy the needs of tea-manufacturing technology preferably, improve tea leaf quality, reduce the fluctuation of load amplitude of motor and whole drive system simultaneously, reduce maximum load and maximum instantaneous power output.
Description of drawings
Fig. 1 is the drive mechanism schematic diagram of an embodiment of the utility model, the driven gear of non-circular gear mechanism is directly installed on the tea arbor among the figure, and non-circular gear mechanism is the gear mechanism of forming with two numbers of teeth and the elliptic gear that modulus equates, eccentric ratio e is identical.
Fig. 2 is the utility model Fig. 1 embodiment non-circular gear mechanism when being the gear mechanism of forming with the elliptic gear that two numbers of teeth and modulus equate, eccentric ratio e is identical, the angle phi of driving gear
1With non-circular gear mechanism gearratio i
12(i
12=ω
1/ ω
2) relation curve.
Fig. 3 is that its non-circular gear mechanism of the utility model is when being the gear mechanism of forming with two deformed elliptic gears, as deformation coefficient m
1≠ m
2, gear 1 rotates the cycle and the transmission ratio function i in a week
12Cycle when equating, the angle phi of gear 1
1With non-circular gear mechanism gearratio i
12Relation curve.
Fig. 4 is that its non-circular gear mechanism of the utility model is the gear mechanism that elliptic gear and deformed elliptic gear conjugation are formed, and the deformed elliptic gear among the figure is the divalence elliptic gear.
Fig. 5 is the kinematic sketch of its non-circular gear mechanism of the utility model two embodiment when being the non-circular gear fixed shaft gear train, and last figure is three gear two-stage transmission non-circular gear mechanism kinematic sketch, and figure below is four gear two-stage transmission non-circular gear mechanism kinematic sketch.
Fig. 6 is the kinematic sketch of another embodiment of the utility model.The driven gear of non-circular gear mechanism is that 1: 1 chain transmission drives the tea arbor indirectly by gearratio.Slack list at chain is provided with regulating wheel, does not draw among the figure.
Among the figure: 1, non-circular gear mechanism driving gear, 2, the non-circular gear mechanism driven gear, 3, the tea arbor, 4, fry tool, 5, frying pan, 6, decelerator, 6.1, decelerator input belt wheel, 7, chain, 7.1, drive sprocket, 7.2, driven sprocket, 7.3, regulating wheel, 8, clutch, 9, gear, 10.1, elliptic gear, 10.2, the second order deformed elliptic gear.
The specific embodiment
The utility model is described in further detail below in conjunction with drawings and Examples.
Shown in Figure 1, preferred embodiment of the utility model, tea machine gear ratio transmission device is made up of non-circular gear mechanism and chain-wheel mechanism, clutch.Its driving-chain is decelerator → chain-drive mechanism → clutch → non-circular gear mechanism → tea arbor.The driven gear 2 of frying tool 4 and non-circular gear mechanism is fixed on the tea arbor 3, driving gear 1 is installed on the jackshaft, 7.2 of driving gear 1 and driven sprockets are provided with clutch, chain-drive mechanism is provided with regulating wheel 7.3, the drive sprocket 7.1 that is installed on the decelerator 6 is unequal with the number of teeth of driven sprocket 7.2, thereby prevents the decelerator uneven wear.
Non-circular gear mechanism among Fig. 1 is made up of with the elliptic gear that modulus equates, eccentric ratio e is identical a pair of number of teeth, the pitch curve of elliptic gear is oval, this long axis of ellipse radius is that a, minor axis radius are that b, oval symmetrical centre are c to the distance of focus, promptly oval eccentric ratio e=c/a.Two elliptic gears are the centre of gyration with focus separately, and the gear pair center of rotation is apart from A
0Equal long axis of ellipse, i.e. A
0=2a.The maximum transmission ratio i of elliptic gear mechanism
12Max and minimum transmission i
12The ratio of min equals the maximum instantaneous angular velocity omega of tea arbor
2Max and minimum instantaneous angular velocity ω
2The ratio of min is represented (K=ω with K
2Max/ ω
2Min=i
12Max/i
12Min).Geometric center O when two gears
1, O
2With the center of rotation of two gears on same straight line, as shown in the figure during the position, the angle phi of driving gear
1As initial phase angle, initial phase angle is zero, and the instantaneous angular velocity minimum of driven gear 2, tea arbor 3 is fried tool 4 and is positioned at effective frying scope α middle part at this moment.The power of motor output drives initiatively with moving through tape handler, decelerator 6, chain-wheel mechanism, clutch 8 that elliptic gears 1 uniform angular velocity rotates, and stir-fry tool 4 variable angular velocities on driven elliptic gear 2, main shaft 3 and the axle rotate.The transmission ratio function i of this a pair of elliptic gear pair
12=(1-e
2)/(1-2e cos φ
1+ e
2), the maximum instantaneous angular velocity omega of driven gear
2Max=[(1+e)/(1-e)] ω
1, its minimum instantaneous angular velocity ω
2Min=[(1-e)/(1+e)] ω
1
Fig. 2 is to be the angle phi of elliptic gear mechanism driving gear among first embodiment of the utility model
1With elliptic gear transmission ratio i
12(i
12=ω
1/ ω
2) relation curve.The angle phi of visible elliptic gear mechanism driving gear among the figure
1From 0 to 2 π rotates a week, the gearratio i of driving gear and driven gear
12Changing Pattern because the driving gear uniform angular velocity rotates, elliptic gear mechanism driven gear, tea arbor, fry tool and make non-uniform angular velocity by the transmission ratio function Changing Pattern and rotate.
In order further to clearly demonstrate present embodiment, introduce the actual relevant situation that makes use-case of a present embodiment below: according to the needs of tea-manufacturing technology, this actual use-case tea arbor maximum instantaneous angular velocity omega when frying the tool idle stroke that makes
2Max fries the minimum instantaneous angular velocity ω that has when imitating the frying angular range
2The twice of min, i.e. K=ω
2Max/ ω
2Min=2 is determined the eccentricity of elliptic gear by K
The number of teeth z of two gears of elliptic gear pair and modulus m can be selected by structure needs and requirement of strength, now select the elliptic gear of number of teeth z=35, modulus m=3 for use.The number of teeth and modulus by gear, the pitch curve perimeter L of elliptic gear=π mz=π * 3 * 35, according to higher mathematics special function theory, oval perimeter L is represented with elliptic integral of the second kind, can calculate elliptic gear pitch curve major axis radius a=52.8914, elliptic gear pitch curve minor axis radius by the table of integrals of oval perimeter L or infinite series expression formula and eccentric ratio e
Eccentric throw c=a * e=9.075, center of rotation is apart from A
0=2a=105.783.Drive sprocket 7.1 numbers of teeth of chain-wheel mechanism are 34 teeth, and driven sprocket 7.2 numbers of teeth are 36 teeth.
Its non-circular gear mechanism of the utility model tea machine gear ratio transmission device can also be the following specific embodiment:
Its non-circular gear mechanism of tea machine gear ratio transmission device can also be one group of deformed elliptic gear.Fig. 3 has represented that non-circular gear mechanism is a deformed elliptic gear, and deformation coefficient m
1≠ m
2, driving gear rotates all transmission ratio function i
12When changing one-period, the angle phi of deformed elliptic gear mechanism driving gear
1With deformed elliptic gear transmission ratio i
12(i
12=ω
1/ ω
2) relation curve.As seen work as φ among the figure
1=0 and φ
1I during=2 π
12=i
12Max works as φ
1=π/m
1The time i
12=i
12Min, the unequal deformed elliptic gear gearratio of deformation coefficient changes by asymmetric rule, can realize that gearratio presses the variable ratio transmission that asymmetric rule changes, transmission ratio function i when being elliptic gear mechanism with Fig. 2 non-circular gear mechanism
12With φ
1The relation curve difference of symmetry.
Its non-circular gear mechanism of tea machine gear ratio transmission device can also be one group of non-circle a--circular gear, and non-circle--circular gear pitch curve is made up of arc section and non-circular curve smooth connection.Gearratio was a constant when arc section of--arc section of circular gear and driven non-circle--circular gear meshed in the gear ratio transmission, when the non-circle of the active of non-circular gear mechanism.
The non-circular gear mechanism of tea machine gear ratio transmission device can also be one group of gear mechanism of being made up of eccentric gear and conjugation non-circular gear.
The non-circular gear mechanism of tea machine gear ratio transmission device can also be the gear mechanism of forming with elliptic gear and deformed elliptic gear, is illustrated in figure 4 as the non-circular gear mechanism that elliptic gear 10.1 and deformed elliptic gear 10.2 are formed.Deformed elliptic gear 10.2 among Fig. 4 is second order elliptic gears, also can be three rank elliptic gears, quadravalence elliptic gear etc.But should consider of the influence of the gear mechanism of elliptic gear and multistage deformed elliptic gear composition to mean speed.For example use the gear mechanism of elliptic gear and second order deformed elliptic gear composition, the number of teeth of second order deformed elliptic gear and pitch curve length are the twice of elliptic gear, the second order deformed elliptic gear rotates all pitch curve radius vector r and changes two cycles, and the elliptic gear that meshes with its changeed for two weeks.When elliptic gear is that driven gear is when being directly installed on the tea arbor, all make non-uniform angular velocity in each week that elliptic gear, tea arbor, stir-fry tool rotate and rotate the variation one-period by non-circular gear mechanism gearratio rule, but mean speed has increased by one times, so the input speed of the gear mechanism formed of elliptic gear and divalence deformed elliptic gear 1/2nd when should be the identical elliptic gear of a pair of number of teeth; When elliptic gear is a driving gear, when the second order deformed elliptic gear is driven gear, elliptic gear rotated for two weeks, the second order deformed elliptic gear turns over a week, but its angular speed is done non-uniform angular velocity rotation by the gearratio rule and has been changed two cycles, between second order deformed elliptic gear and tea arbor, also should be provided with a stable drive ratio and gearratio i
12=1: 2 gear mechanism or chain-drive mechanism.
Deformation coefficient m when deformed elliptic gear
1=m
2=m, and m is during greater than 1 integer, can obtain various oval gears, the non-circular gear mechanism of tea machine gear ratio transmission device can also be the gear mechanism of forming with oval gear.The embodiment of the driving-chain between its tea arbor and the decelerator, and it is same that the non-circular gear transmission mechanism of forming with elliptic gear and deformed elliptic gear is set on the driving-chain between tea arbor and the decelerator, should consider of the influence of the exponent number of oval gear, and oval gear mechanism driven gear rotates the cycle and the transmission ratio function i in a week to mean speed
12The relation in cycle.
Value (K=ω as K
2Max/ ω
2Min=i
12Max/i
12When min) big, the non-circular gear mechanism of tea machine gear ratio transmission device can also be the non-circular gear fixed shaft gear train.Fig. 5 is the kinematic sketch of its non-circular gear mechanism of the utility model two embodiment when being the non-circular gear fixed shaft gear train, and last figure is three gear two-stage transmission non-circular gear mechanism kinematic sketch, and figure below is four gear two-stage transmission non-circular gear mechanism kinematic sketch.
Non-circular gear mechanism among Fig. 1 is except being elliptic gear mechanism, also can be the non-circular gear mechanism of other type, as gear mechanism, non-circle--circular gear gear mechanism, eccentric gear and conjugation non-circular gear gear mechanism, the non-circular gear fixed shaft gear train of deformed elliptic gear mechanism, elliptic gear and deformed elliptic gear composition.But because driven non-circular gear is fixedly installed on the tea arbor, driven non-circular gear must be a single order, and promptly driven gear turns over all gearratio variation one-periods.
Fig. 6 is the kinematic sketch of another embodiment of the utility model.Tea machine gear ratio transmission device is made up of gear mechanism, clutch, non-circular gear mechanism and chain-wheel mechanism.Its driving-chain is decelerator → gear mechanism → clutch → non-circular gear mechanism → chain wheel driving mechanism → tea arbor, non-circular gear 1 is formed non-circular gear mechanism with non-circular gear 2, driven gear 2 is installed in the same rotating shaft with drive sprocket 7.1, driven sprocket 7.2 is fixed on the tea arbor 3, is provided with regulating wheel (not drawing among the figure) in the slack list of chain.Decelerator 6 rotates by driving gear 1 uniform angular velocity that gear drive 9, clutch 8 drive non-circular gear mechanism, and driven gear 2, sprocket wheel, tea arbor, stir-fry tool variable angular velocity rotate.The driving wheel 9 of second embodiment middle gear transmission mechanism is unequal to prevent deceleration worm gear uneven wear with driven pulley 9 numbers of teeth.
The ordinary gear transmission mechanism of stable drive ratio also can be set between non-circular gear mechanism and the tea arbor, and its driving-chain is the ordinary gear transmission mechanism → tea arbor of decelerator → gear mechanism → clutch → non-circular gear mechanism → stable drive ratio.The driven gear 2 of non-circular gear mechanism is installed in the same rotating shaft with the driving gear of the ordinary gear transmission mechanism of stable drive ratio, and the driven gear of the ordinary gear transmission mechanism of stable drive ratio is fixed on the tea machine main shaft.
In embodiment illustrated in fig. 6, its non-circular gear mechanism driven gear rotates a week, angular speed is made non-uniform angular velocity by non-circular gear mechanism gearratio Changing Pattern and is rotated and change one-period, and engagement transmission mechanism (gear mechanism or the chain wheel driving mechanism) driving wheel of the stable drive ratio that is provided with between non-circular gear mechanism and the tea arbor equates to be that their gearratio equals 1 with the driven pulley number of teeth.If the non-circular gear mechanism driven gear rotates a week, angular speed is made non-uniform angular velocity by non-circular gear mechanism gearratio Changing Pattern and is rotated a variation Integer n cycle (for example driven gear is second order deformed elliptic gear, three rank deformed elliptic gears etc.), the engagement transmission mechanism of the stable drive ratio that is provided with between non-circular gear mechanism and the tea arbor (gear mechanism or chain wheel driving mechanism) driving wheel and driven pulley gear ratio equal n, i.e. their gearratio i
12=1: n.
Between decelerator and the non-circular gear mechanism, remove that the already mentioned decelerator of above embodiment drives non-circular gear mechanism by chain-wheel mechanism, clutch and decelerator drives non-circular gear mechanism by gear drive, clutch, also can be decelerator directly or drive the driving gear of non-circular gear mechanism by clutch.
Claims (10)
1. tea machine variable ratio transmission device, be arranged on the tea machine variable ratio transmission device between tea arbor and the decelerator, form by the transmission parts, it is characterized in that: the tea machine variable ratio transmission device between tea arbor and decelerator is provided with the non-circular gear transmission mechanism, the pitch curve of the gear that non-circular gear mechanism is engaged with each other is determined by noncircular gear pair transmission ratio function given by the tea arbor characteristics of motion and two gear centres distance, being connected by driven gear of the driven gear of non-circular gear mechanism and tea arbor turns over all gearratio period of change numbers and decides, when gearratio changes one-period, driven gear directly is fixedly mounted on the tea arbor, between perhaps driven non-circular gear and main shaft one group of number of teeth is set and equates, it is the engagement transmission mechanism that gearratio equals 1; When gearratio changes an Integer n cycle, be provided with one group of engagement transmission mechanism between driven non-circular gear in the non-circular gear transmission mechanism and main shaft, its driving wheel and driven pulley gear ratio equal n, i.e. their gearratio i
12=1: n.
2. tea machine variable ratio transmission device according to claim 1 is characterized in that: described non-circular gear transmission mechanism is the gear mechanism of forming with two numbers of teeth and the elliptic gear that modulus equates, eccentric ratio e is identical.
3. tea machine variable ratio transmission device according to claim 1 is characterized in that: described non-circular gear transmission mechanism is the gear mechanism of forming with two deformed elliptic gears.
4. tea machine variable ratio transmission device according to claim 1 is characterized in that: described non-circular gear transmission mechanism is the gear mechanism of forming with elliptic gear and deformed elliptic gear.
5. tea machine variable ratio transmission device according to claim 1, it is characterized in that: described non-circular gear transmission mechanism is with two non-circles--the gear mechanism that circular gear is formed, the pitch curve of non-circle--circular gear is made up of arc section and the smooth connection of non-circular curve section.
6. tea machine variable ratio transmission device according to claim 1 is characterized in that: described non-circular gear transmission mechanism is the gear mechanism of forming with eccentric gear and conjugation non-circular gear.
7. tea machine variable ratio transmission device according to claim 1 is characterized in that: described non-circular gear mechanism is the gear mechanism of forming with oval gear.
8. tea machine variable ratio transmission device according to claim 1, it is characterized in that: described non-circular gear transmission mechanism is the non-circular gear fixed shaft gear train.
9. according to the described tea machine of any one claim variable ratio transmission device in the claim 1 to 8, it is characterized in that: the clutch of described tea machine variable ratio transmission device is arranged on the driving-chain between decelerator and the non-circular gear transmission mechanism.
10. according to the described tea machine of any one claim variable ratio transmission device in the claim 1 to 8, it is characterized in that: the engagement transmission mechanism that is provided with on the driving-chain between described non-circular gear transmission mechanism and the decelerator, the tooth number of its driving wheel and driven pulley differs several teeth.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU200720152739XU CN201032823Y (en) | 2007-05-31 | 2007-05-31 | Tea machine transmission device with varied transmission ratio |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU200720152739XU CN201032823Y (en) | 2007-05-31 | 2007-05-31 | Tea machine transmission device with varied transmission ratio |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201032823Y true CN201032823Y (en) | 2008-03-12 |
Family
ID=39193713
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU200720152739XU Expired - Fee Related CN201032823Y (en) | 2007-05-31 | 2007-05-31 | Tea machine transmission device with varied transmission ratio |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201032823Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103508221A (en) * | 2013-09-25 | 2014-01-15 | 马钢(集团)控股有限公司 | Swing-type belt distributing device and method for determining sizes of gears of elliptical gear case of swing-type belt distributing device |
| CN108916318A (en) * | 2018-07-18 | 2018-11-30 | 武汉理工大学 | A kind of design method and its mechanical driving device of the change center away from non-circular gear pair |
-
2007
- 2007-05-31 CN CNU200720152739XU patent/CN201032823Y/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103508221A (en) * | 2013-09-25 | 2014-01-15 | 马钢(集团)控股有限公司 | Swing-type belt distributing device and method for determining sizes of gears of elliptical gear case of swing-type belt distributing device |
| CN103508221B (en) * | 2013-09-25 | 2015-10-07 | 马钢(集团)控股有限公司 | The defining method of a kind of pendulum-type leather belt material distributing device and elliptic gear case gear size thereof |
| CN108916318A (en) * | 2018-07-18 | 2018-11-30 | 武汉理工大学 | A kind of design method and its mechanical driving device of the change center away from non-circular gear pair |
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|---|---|---|---|
| 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: 20080312 Termination date: 20110531 |