CN101251174B - Planetary multilevel gear drive mechanism - Google Patents
Planetary multilevel gear drive mechanism Download PDFInfo
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- CN101251174B CN101251174B CN2008100652387A CN200810065238A CN101251174B CN 101251174 B CN101251174 B CN 101251174B CN 2008100652387 A CN2008100652387 A CN 2008100652387A CN 200810065238 A CN200810065238 A CN 200810065238A CN 101251174 B CN101251174 B CN 101251174B
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Abstract
The invention discloses a planetary type multilevel gear transmission mechanism, comprising a sun gear set used for the input and output of power, the speed change and the turning, a planetary gear set used to form the speed difference between sun gears, a planet carrier sharing the same shaft center with the sun gear set and a planetary shaft arranged on the planet carrier by a bearing, wherein the sun gear set consists of multilevel sun gears having the same shaft center, including a first level sun gear, a second level sun gear and a third level sun gear; the first level sun gear comprisesa first level gear shaft arranged on the same shaft center; the second level sun gear is arranged on the same shaft center; the third level sun gear is sleeved on the second level sun gear by a bearing; the planetary gear set comprises a first level planetary gear meshed with the first level sun gear, a second level planetary gear meshed with the second level sun gear and a third level planetary gear meshed with the third level sun gear. The mechanism has the advantages of realizing functions of the on-off between the power input and the power output, the same direction variable speed transmission, the reverse direction variable speed transmission and the multilevel simultaneous output, etc.
Description
Technical field
The present invention relates to a kind of variable transmission mechanism with planetary gear construction.
Background technique
The speed change gear that prior art utilizes planetary gear mechanism to realize, be widely used in mechanical transmission industries such as various vehicles, machinery, more planetary gear mechanism adopts sun gear, planetary pinion, annulus internal gear to make up and realizes speed changing function, various vehicles and other Transport Machinery adopt two groups of clutches to cooperate with two groups of planetary gear mechanisms mostly, realize the function of powerdriven clutch, equidirectional transmission and transmission in the other direction.At present, more battle wagon, heavy goods vehicle, engineering machinery and defence equipment etc. also are equipped with fluid torque converter, realize electrodeless variable-speed, improve the passing ability of locomotive, reduce shift number, improve comfort of drivers and passengers, prolong the life-span of motor and gearing.But the complex structure of said apparatus, the processing request height, the cost of production height, maintenance difficult, the transmission efficiency of motor is low, energy consumption height, user cost height.
Along with further developing of industrial automation process, the application area of speed change gear is more extensive, develops a kind of simple in structure, slewing range is big, applied range, good combination property, with low cost, can break through the gear that has transmission technology now, be a direction of current mechanical transmission industry.
Summary of the invention
Technical problem to be solved by this invention is: a kind of planetary multilevel gear drive mechanism is provided, this driving mechanism has simple in structure, can also realize clutch, equidirectional speed change transmission and functions such as reverse speed change transmission and multistage output simultaneously between power input and the power output.
For solving the problems of the technologies described above, the present invention adopts following technological scheme: a kind of planetary multilevel gear drive mechanism comprises:
The sun gear group that is used for power input output speed change, break-in;
Be used to form the planetary gear set of speed discrepancy between sun gear;
Planet carrier with the common axle center of sun gear group;
Be located at planet axis on the planet carrier by means of bearing;
Described sun gear group is made of the multistage sun gear in common axle center, comprising one-level sun gear, secondary sun gear and three grades of sun gears; The one-level sun gear comprises the one-level gear shaft that is in described common shaft core position, and secondary sun gear is located at described common axle in the heart, and three grades of sun gears are located on the secondary sun gear by means of bearing housing;
Described planetary gear set comprise one with the primary planet pinion of one-level sun gear engagement, one secondary planetary gear and third-level planetary gear that meshes with three grades of sun gears with the secondary sun gear engagement, and described primary planet pinion, secondary planetary gear and third-level planetary gear are all coaxial is fixedly mounted on the planet axis.
Preferably: described mechanism comprises input shaft, and arbitrary grade of sun gear in described planet carrier or the described multistage sun gear connects input shaft.
Preferably: described mechanism comprises output shaft, and arbitrary grade of sun gear in described planet carrier or the described multistage sun gear connects output shaft.
Preferably: described mechanism also comprises the oil hydraulic pump that is used to brake, and any two are connected with oil hydraulic pump in described planet carrier, one-level sun gear, secondary sun gear and the three grades of sun gears.
Preferably: any two are connected with oil hydraulic pump by gear mesh in described planet carrier, one-level sun gear, secondary sun gear and the three grades of sun gears.
Preferably: described mechanism also comprises the brake disc that is used to brake, and any two are connected with brake disc in described planet carrier, one-level sun gear, secondary sun gear and the three grades of sun gears.
Preferably:
Described sun gear group also comprises:
Level Four sun gear and Pyatyi sun gear that common axle center is arranged;
All be connected on the described planet axis, with the level Four planetary pinion of level Four sun gear engagement and with the Pyatyi planetary pinion of Pyatyi sun gear engagement;
Wherein, the level Four sun gear is connected on described three grades of sun gears by bearing housing, and the Pyatyi sun gear is connected on the level Four sun gear by bearing housing; Sun gears at different levels all connect brake disc.
Preferably: every grade of planetary pinion is arranged by at least two gears and is constituted.
The invention has the beneficial effects as follows: compared to existing technology, any all can use as input, output and control gear in the planet carrier of planetary multilevel gear drive mechanism of the present invention and the sun gear at different levels, by controlling the rotating speed of sun gears at different levels and planet carrier, make and realize clutch, equidirectional speed change transmission and speed change transmission in the other direction between power input and the power output, it is simple in structure, same structure possesses multiple function, the variable speed drive of the field power such as vehicle, vessel, machinery and defence equipment that can be used for varying in size.
The present invention is described in further detail below in conjunction with accompanying drawing.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention one.
Fig. 2 is the structural representation of the embodiment of the invention two.
Fig. 3 is the structural representation of the embodiment of the invention three.
Fig. 4 is the structural representation of the embodiment of the invention four.
Fig. 5 is the structural representation of the embodiment of the invention five.
Fig. 6 is embodiment two the resistance type stepless speed changes devices and the structural representation of controlling method.
Embodiment
The invention provides a kind of planetary multilevel gear drive mechanism.This driving mechanism comprises: the sun gear group that is used for power input output speed change, break-in; Be used to form the planetary gear set of speed discrepancy between sun gear; Planet carrier with the common axle center of sun gear group; Be located at planet axis on the planet carrier by means of bearing; The sun gear group is made of the multistage sun gear in common axle center, comprising one-level sun gear, secondary sun gear and three grades of sun gears; The one-level sun gear comprises the one-level gear shaft that is in common shaft core position, and secondary sun gear is located at common axle in the heart, and three grades of sun gears are located on the secondary sun gear by means of bearing housing; Planetary gear set comprises the primary planet pinion, a secondary planetary gear and the third-level planetary gear that meshes with three grades of sun gears that meshes with secondary sun gear that mesh with the one-level sun gear.
Embodiments of the invention one structure as shown in Figure 1.
By control one-level sun gear 2, make planet carrier 1 realize the speed change transmission simultaneously and between secondary sun gear 8 and three grades of sun gears 7.By control secondary sun gear 8, make planet carrier 1 realize the speed change transmission simultaneously and between one-level sun gear 2 and three grades of sun gears 7.By controlling three grades of sun gears 7, make between 1 while of planet carrier and one-level sun gear 2 and the secondary sun gear 8 and realize the speed change transmission.By control planet carrier 1, make one-level sun gear 2 realize the speed change transmission simultaneously and between secondary sun gear 8 and three grades of sun gears 7.The ratio of the present invention by realizing between certain one-level sun gear (or planet carrier) of control and the gear at different levels, make and realize clutch, equidirectional speed change transmission and speed change transmission in the other direction between power input and the power output, same structure possesses multiple function, the transmission device of the field power such as vehicle, vessel, machinery and defence equipment that can be used for varying in size.
The certain applications speed of this planetary multilevel gear drive mechanism is as follows than calculation method:
If A is the number of teeth of one-level sun gear, B is the number of teeth of primary planet pinion, and C is the number of teeth of secondary sun gear, and D is the number of teeth of secondary planetary gear, and E is the number of teeth of three grades of sun gears, and F is the number of teeth of third-level planetary gear.
Example 1: when A is fixed, planet carrier whenever turn around and secondary sun gear between velocity ratio calculate according to following mode:
Velocity ratio=((A ÷ B) * D-C) ÷ C
Then planet carrier whenever turn around and three grades of sun gears between velocity ratio calculate according to following mode:
Velocity ratio=((A ÷ B) * F-E) ÷ E
Example 2: when C is fixed, planet carrier whenever turn around and the one-level sun gear between velocity ratio calculate according to following mode:
Velocity ratio=((C ÷ D) * B-A) ÷ A
Then planet carrier whenever turn around and three grades of sun gears between velocity ratio calculate according to following mode:
Velocity ratio=((C ÷ D) * F-E) ÷ E
Example 3: when E is fixed, planet carrier whenever turn around and the one-level sun gear between velocity ratio calculate according to following mode:
Velocity ratio=((E ÷ F) * B-A) ÷ A
Then planet carrier whenever turn around and secondary sun gear between velocity ratio calculate according to following mode:
Velocity ratio=((E ÷ F) * D-C) ÷ C
Velocity ratio between this planetary multilevel gear drive mechanism gears at different levels can be divided three classes:
When velocity ratio is positive number, opposite direction transmission between input shaft and the output shaft.
When velocity ratio is zero, not transmission between input shaft and the output shaft.
When velocity ratio is negative, equidirectional transmission between input shaft and the output shaft.
Embodiments of the invention two structures are referring to Fig. 2 and Fig. 6.
Embodiment two is structures of resistance type stepless speed changes devices.Referring to Fig. 2, the planet carrier 1 of above-mentioned planetary multilevel gear drive mechanism is connected with body 500 by bearing.Planet carrier 1 is as input, and one-level sun gear 2 is as output.The rotating shaft of fixedly connected first oil hydraulic pump 100 on three grades of sun gears 7, the shell of first oil hydraulic pump 100 is fixedlyed connected with body 500.The rotating shaft of fixedly connected second oil hydraulic pump 101 on secondary sun gear 8, the shell of second oil hydraulic pump 101 is fixedlyed connected with body 500.
Referring to Fig. 6, the filler opening of first oil hydraulic pump 100 is connected with the outlet of the first one-way valve a1, and the filler opening of second oil hydraulic pump 101 is connected with the outlet of the 3rd one-way valve a3.The inlet parallel of the first one-way valve a1 and the 3rd one-way valve a3 and the hydraulic oil of fuel reserve tank are connected, and the oil outlet of first oil hydraulic pump 100 is connected with the first pressure transducer c1 by a tee union.The control power supply of the first pressure transducer c1 is connected with controller, and another interface on the tee union is connected with the filler opening of the second one-way valve a2.The oil outlet of second oil hydraulic pump 101 also is connected with the second pressure transducer c2 by a tee union, and the control power supply of the second pressure transducer c2 is connected with controller, and another interface on the tee union is connected with the filler opening of the 4th one-way valve a4.The oil outlet of the second one-way valve a2 is connected on the interface P of the first hydrovalve b1, the interface T sealing on the first hydrovalve b1, and the oil outlet of the 4th one-way valve a4 is connected on the interface P of the second hydrovalve b2, the interface T sealing on the second hydrovalve b2.The first hydrovalve b1 is connected with the filler opening of cooling unit with the interface B on the second hydrovalve b2 is in parallel.The oil outlet of cooling unit and fuel reserve tank are connected.The first hydrovalve b1 is connected with the oil inlet P of hydraulic proportion valve with the interface A on the second hydrovalve b2 is in parallel, the interface T sealing of hydraulic proportion valve, the oil outlet A of hydraulic proportion valve and the filler opening of cooling unit are connected in parallel, and the control power supply of hydraulic proportion valve and two hydrovalves is connected with corresponding controller respectively.Drive planetary pinions at different levels when corresponding sun gears at different levels rotate when input drives planet carrier 1, when two hydrovalves all were in no working state, interface P and interface B on two hydrovalves all connected, and the oil outlet of two oil hydraulic pumps is all not controlled.When the resistance of being exported, the rotation of one-level sun gear 2 is controlled, transmission secondary sun gear 8 and three grades of sun gears 7 drive corresponding first oil hydraulic pump 100 and 101 rotations of second oil hydraulic pump, and then not transmission between input and the output is in separated state.Controlled when in running order as the first hydrovalve b1, interface P on the first hydrovalve b1 and interface A connect, and the oil outlet of first oil hydraulic pump 100 is subjected to hydraulic proportion valve control, the flow of controller control hydraulic proportion valve.The rotating speed of first oil hydraulic pump 100 is subjected to resistance (three grades of sun gears 7 when stationary state, the velocity ratio that planet carrier whenever turns around with one-level sun gear 2 is a negative).During resistance that the resistance that first oil hydraulic pump 100 is subjected to is subjected to greater than output, begin to realize transmission between three grades of sun gears 7 and the one-level sun gear 2, then same direction is rotated between output and the input, and the second hydrovalve b2 is not controlled, begin to realize transmission equally between three grades of sun gears 7 and the secondary sun gear 8, and drive 101 rotations of second oil hydraulic pump and be not subjected to resistance, be in driven state.The flow of controller control hydraulic proportion valve is more little, the resistance that first oil hydraulic pump 100 is subjected to is big more, its rotating speed step-down, the rotating speed of the output and second oil hydraulic pump 101 then uprises, and the high more resistance that is subjected to relatively of output speed is big more, and the pressure that first oil hydraulic pump 100 produces is also big more.If during the pressure that the resistance that is subjected to of output produces greater than first oil hydraulic pump 100, the rotating speed of first oil hydraulic pump 100 is corresponding to uprise, the relative step-down of rotating speed of the output and second oil hydraulic pump 101, the first pressure transducer c1 reaches controller with the pressure data of first oil hydraulic pump 100, controller is followed the height according to required output speed, control the flow size of hydraulic proportion valve again, the rotation of controlling first oil hydraulic pump 100 is subjected to corresponding resistance, makes the rotating speed of output or high or low.When if output speed is greater than the rotating speed of one-level sun gear 2 owing to coherence power, the first one-way valve a1 that is connected with oil outlet by first oil hydraulic pump, 100 filler openings and the second one-way valve a2 limit first oil hydraulic pump 100 can not backward rotation, make output speed be subjected to importing the restriction of driving power device, realize unidirectional stepless change transmission between input and the output.When the second hydrovalve b2 controlled when in running order, interface P on the second hydrovalve b2 and interface A connect, the oil outlet of second oil hydraulic pump 101 is subjected to hydraulic proportion valve control, the flow of controller control hydraulic proportion valve, the rotating speed of second oil hydraulic pump 101 is subjected to resistance (two sun gears 8 when stationary state, the velocity ratio that planet carrier whenever turns around with one-level sun gear 2 is a positive number).During resistance that the resistance that second oil hydraulic pump 101 is subjected to is subjected to greater than output, begin to realize transmission between secondary sun gear 8 and the one-level sun gear 2, then opposite direction rotates between output and the input, and the first hydrovalve b1 is not controlled, begin to realize transmission equally between secondary sun gear 8 and three grades of sun gears 7, and drive 100 rotations of first oil hydraulic pump and be not subjected to resistance, be in driven state.The flow of controller control hydraulic proportion valve is more little, and the resistance that second oil hydraulic pump 101 is subjected to is big more, its rotating speed step-down, and output and first oil hydraulic pump, 100 rotating speeds then uprise, and the high more resistance that is subjected to of output speed is big more, and the pressure that second oil hydraulic pump 101 produces is also big more.If during the pressure that the resistance that is subjected to of output produces greater than second oil hydraulic pump 101, the rotating speed of second oil hydraulic pump 101 is corresponding to uprise, the relative step-down of rotating speed of the output and first oil hydraulic pump 100, the second pressure transducer c2 reaches controller with the pressure data of second oil hydraulic pump 101, controller is followed the height according to required output shaft rotating speed, control the flow size of hydraulic proportion valve again, the rotating speed of controlling second oil hydraulic pump 101 is subjected to corresponding resistance, makes the rotating speed of output or high or low.When if output speed is greater than the rotating speed of one-level sun gear 2 owing to coherence power, the 3rd one-way valve a3 that is connected with oil outlet by second oil hydraulic pump, 101 filler openings and the 4th one-way valve a4 limit second oil hydraulic pump 101 can not backward rotation, make output speed be subjected to importing the restriction of driving power device, realize rightabout stepless change transmission between input and the output.The resistance size that this structure is subjected to by controlling two oil hydraulic pumps, the rotating speed of restriction secondary sun gear 8 and three grades of sun gears 7, make and realize clutch, the transmission of same direction speed change and speed change transmission in the other direction between power input and the power output, it is simple in structure, same structure possesses multiple function, the advantage that has also possessed fluid torque converter simultaneously is applicable to power-actuated infinitely variable speed transmissions in field such as the vehicle that varies in size, vessel, machinery and defence equipments.
Wherein, the oil outlet of two oil hydraulic pumps can also be connected with machinery control hydrovalve with other Electromagnetic Control hydrovalve.
Wherein, the oil outlet of two oil hydraulic pumps can also directly be connected with two hydraulic proportion valves respectively.
Wherein, the flow of the oil outlet of two oil hydraulic pumps can also be connected with the servo ratio control valve with other flow control valve.
Wherein, the flow of the oil outlet of two oil hydraulic pumps can also be connected with oil hydraulic motor with other speed change flow pump.
Embodiments of the invention three are referring to Fig. 3.
Accompanying drawing 3 is structural representations of planetary multilevel gear drive mechanism embodiment three of the present invention.On embodiment two basis, three grades of sun gears 7 are connected with body 500 by bearing with planet carrier 1.Planet carrier 1 is as input, and one-level sun gear 2 is as output.Fixedly connected the 3rd gear 11 on three grades of sun gears 7, one or more first oil hydraulic pump 100 is passed through first gear 9 and the 11 meshing installations of the 3rd gear, the rotating shaft of first oil hydraulic pump 100 is fixedlyed connected with first gear 9, the rotating shaft of first oil hydraulic pump 100 is connected with body 500 by bearing, and the shell of first oil hydraulic pump 100 is fixedlyed connected with body 500.Fixedly connected second gear 10 on secondary sun gear 8, one or more second oil hydraulic pump 101 is passed through the 4th gear 12 and the 10 meshing installations of second gear, the rotating shaft of second oil hydraulic pump 101 is fixedlyed connected with the 4th gear 12, the rotating shaft of second oil hydraulic pump 101 is connected with body 500 by bearing, and the shell of second oil hydraulic pump 101 is fixedlyed connected with body 500.
Embodiments of the invention four are referring to Fig. 4.
Accompanying drawing 4 is planetary multilevel gear drive mechanism embodiments four of the present invention---the structural representation of utmost point speed change engaging and disengaging gear is arranged.One-level sun gear 2 is connected with planet carrier 1 by bearing, secondary sun gear 8 is connected with star frame 1 by bearing, three grades of sun gears 7 are connected with secondary sun gear 8 by bearing, and one-level sun gear 2 is engaged with primary planet pinion 4, constitute the one-level gear drive.Secondary sun gear 8 is engaged with secondary planetary gear 5, constitutes the secondary gear driving mechanism.Three grades of sun gears 7 are engaged with third-level planetary gear 6, constitute the tertiary gear driving mechanism.Primary planet pinion 4, secondary planetary gear 5 and third-level planetary gear 6 coaxial being fixedly mounted on the planet axis 3, planet axis 3 is connected with planet carrier 1 by bearing.Body 500 is connected with three grades of sun gears 7 with one-level sun gear 2 by bearing.Corresponding first braking device 201 of installing of the periphery of fixedly connected first brake disc, 21, the first brake discs 21 on three grades of sun gears 7, corresponding second braking device 202 of installing of fixedly connected second brake disc, 22, the second brake discs, 22 peripheries on secondary sun gear 8.Planet carrier 1 is as input, and one-level sun gear 2 is as output.By the rotation of three grades of sun gears of braking device control and secondary sun gear, make and realize clutch, the transmission of same direction speed change and speed change transmission in the other direction between power input and the power output.
The embodiments of the invention Wucan is seen Fig. 5.
Accompanying drawing 5 is that planetary multilevel gear drive mechanism embodiment five of the present invention---many gears have the structural representation of utmost point speed change gear.
Corresponding first braking device 201 of installing of the periphery of fixedly connected first brake disc, 21, the first brake discs 21 on three grades of sun gears 7.Corresponding second braking device 202 of installing of fixedly connected second brake disc, 22, the second brake discs, 22 peripheries on secondary sun gear 8.Corresponding the 3rd braking device 203 of installing of fixedly connected the 3rd brake disc 23, the three brake discs, 23 peripheries on level Four sun gear 15.Corresponding the 4th braking device 204 of installing of fixedly connected the 4th brake disc 24, the four brake discs, 24 peripheries on Pyatyi sun gear 16.On the basis of the foregoing description one, increase level Four or the above sun gear of Pyatyi, and connect brake disc at sun gears at different levels.Control the rotation of sun gears at different levels by braking device, make and realize clutch, the transmission of same direction speed change and speed change transmission in the other direction between power input and the power output.
Said structure, wherein, primary planet pinion, secondary planetary gear, third-level planetary gear, level Four planetary pinion and Pyatyi planetary pinion constitute the gear train of parallel arranged by one, two or more gear, and be meshing with corresponding sun gears at different levels by gear train.
Wherein, any all can use as input, output and control gear in planet carrier and one-level sun gear, secondary sun gear and the three grades of sun gears.
Wherein, planet carrier, one-level sun gear, secondary sun gear, three grades of sun gears, level Four sun gear and Pyatyi sun gears all are connected with drive wheel; Wherein any is as input device, and another is as control gear, and other uses as output unit simultaneously.
Claims (8)
1. planetary multilevel gear drive mechanism comprises:
The sun gear group that is used for power input output speed change, break-in;
Be used to form the planetary gear set of speed discrepancy between sun gear;
Planet carrier with the common axle center of sun gear group;
Be located at planet axis on the planet carrier by means of bearing;
It is characterized in that,
Described sun gear group is made of the multistage sun gear in common axle center, comprising one-level sun gear, secondary sun gear and three grades of sun gears; The one-level sun gear comprises the one-level gear shaft that is in described common shaft core position, and secondary sun gear is located at described common axle in the heart, and three grades of sun gears are located on the secondary sun gear by means of bearing housing;
Described planetary gear set comprise one with the primary planet pinion of one-level sun gear engagement, one secondary planetary gear and third-level planetary gear that meshes with three grades of sun gears with the secondary sun gear engagement, and described primary planet pinion, secondary planetary gear and third-level planetary gear are all coaxial is fixedly mounted on the planet axis.
2. planetary multilevel gear drive mechanism according to claim 1 is characterized in that: described mechanism comprises input shaft, and arbitrary grade of sun gear in described planet carrier or the described multistage sun gear connects input shaft.
3. planetary multilevel gear drive mechanism according to claim 1 is characterized in that: described mechanism comprises output shaft, and arbitrary grade of sun gear in described planet carrier or the described multistage sun gear connects output shaft.
4. planetary multilevel gear drive mechanism according to claim 1, it is characterized in that: described mechanism also comprises the oil hydraulic pump that is used to brake, and any two are connected with oil hydraulic pump in described planet carrier, one-level sun gear, secondary sun gear and the three grades of sun gears.
5. planetary multilevel gear drive mechanism according to claim 1 is characterized in that: any two are connected with oil hydraulic pump by gear mesh in described planet carrier, one-level sun gear, secondary sun gear and the three grades of sun gears.
6. planetary multilevel gear drive mechanism according to claim 1, it is characterized in that: described mechanism also comprises the brake disc that is used to brake, and any two are connected with brake disc in described planet carrier, one-level sun gear, secondary sun gear and the three grades of sun gears.
7. planetary multilevel gear drive mechanism according to claim 1 is characterized in that:
Described sun gear group also comprises:
Level Four sun gear and Pyatyi sun gear that common axle center is arranged;
All be connected on the described planet axis, with the level Four planetary pinion of level Four sun gear engagement and with the Pyatyi planetary pinion of Pyatyi sun gear engagement;
Wherein, the level Four sun gear is connected on described three grades of sun gears by bearing housing, and the Pyatyi sun gear is connected on the level Four sun gear by bearing housing; Sun gears at different levels all connect brake disc.
8. planetary multilevel gear drive mechanism according to claim 1 is characterized in that: every grade of planetary pinion is arranged by at least two gears and is constituted.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2008100652387A CN101251174B (en) | 2008-01-29 | 2008-01-29 | Planetary multilevel gear drive mechanism |
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| CN2008100652387A CN101251174B (en) | 2008-01-29 | 2008-01-29 | Planetary multilevel gear drive mechanism |
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| CN101251174A CN101251174A (en) | 2008-08-27 |
| CN101251174B true CN101251174B (en) | 2010-11-17 |
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| CN109505928A (en) * | 2018-12-30 | 2019-03-22 | 苏州富强科技有限公司 | A kind of secondary planetary gear transmission mechanism for 3D bend glass polishing machine |
| CN110805683A (en) * | 2019-11-20 | 2020-02-18 | 宿州市祁南工贸有限责任公司 | Speed reducer with high conversion rate |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1425860A (en) * | 2001-12-10 | 2003-06-25 | 丰田自动车株式会社 | Automatic speed variator |
| US7211022B2 (en) * | 2004-05-14 | 2007-05-01 | Zf Friedrichshafen Ag | Automatic transmission |
| CN101201096A (en) * | 2007-12-17 | 2008-06-18 | 郭克亚 | Planetary multilevel gear drive mechanism |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10231346A1 (en) * | 2002-07-11 | 2004-01-29 | Zf Friedrichshafen Ag | Multi-speed transmission |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1425860A (en) * | 2001-12-10 | 2003-06-25 | 丰田自动车株式会社 | Automatic speed variator |
| US7211022B2 (en) * | 2004-05-14 | 2007-05-01 | Zf Friedrichshafen Ag | Automatic transmission |
| CN101201096A (en) * | 2007-12-17 | 2008-06-18 | 郭克亚 | Planetary multilevel gear drive mechanism |
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