CN101201096B - Planetary multilevel gear drive mechanism - Google Patents
Planetary multilevel gear drive mechanism Download PDFInfo
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- CN101201096B CN101201096B CN2007101250470A CN200710125047A CN101201096B CN 101201096 B CN101201096 B CN 101201096B CN 2007101250470 A CN2007101250470 A CN 2007101250470A CN 200710125047 A CN200710125047 A CN 200710125047A CN 101201096 B CN101201096 B CN 101201096B
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Abstract
The utility model relates to a planet-type multilevel-gear transmission mechanism which comprises an input shaft, an output shaft, a planet frame firmly connected with the input shaft and sharing the same axis, a planet shaft arranged on the planet frame by a bearing, a planet gear set fixed on the planet shaft, a first-level sun gear fixed on the output shaft as well as a second-level sun gear and a third-level sun gear sleeved on the output shaft. The planet gear set comprises a first-level planet gear engaged with the first-level sun gear, a second-level planet gear engaged with the second-level sun gear and a third-level planet gear engaged with the third-level sun gear. The second-level sun gear is provided with a first flange. The first flange is sleeved on the input shaft. The third-level sun gear is sleeved on the first flange and provided with a second flange. The second flange is sleeved on the first flange. The invention can be used for the variable speed power transmission in the field like vehicles, ships, machinery devices and national defense devices, etc. The invention has a simple structure and can realize the clutching between input and output, a same direction variable speed transmission and a reverse direction variable speed transmission.
Description
Technical field
The present invention relates to a kind of variable transmission mechanism with planetary gear construction.
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 stepless change, 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.
Technical problem to be solved by this invention is: a kind of planetary multilevel gear drive mechanism is provided, and this driving mechanism has simple in structure, can also realize the functions such as clutch, equidirectional speed change transmission and reverse speed change transmission 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 input shaft, output shaft, the planet carrier of fixedlying connected with the input shaft concentric, is located at planet axis on the planet carrier, is fixedly arranged on planetary gear set on the planet axis, is fixedly arranged on one-level sun gear on the output shaft, is located at secondary sun gear and three grades of sun gears on the described input shaft by means of bearing housing by means of bearing; Wherein, described planetary gear set comprises a primary planet pinion that meshes with the one-level sun gear, a secondary planetary gear and a third-level planetary gear that meshes with three grades of sun gears that meshes with secondary sun gear, also be installed with first flange of external connection on the described secondary sun gear, described first flange is located on the input shaft by means of bearing housing, described three grades of sun gears are located on first flange by means of bearing housing, also be installed with second flange of external connection on described three grades of sun gears, described second flange is located on first flange by means of bearing housing.
Preferably: described first flange, second flange connect oil hydraulic pump.The resistance size that this structure is subjected to by controlling two oil hydraulic pumps, the rotating speed of restriction secondary sun gear and three grades of sun gears, 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.
Preferably: described first flange, second flange connect brake disc.
Preferably: described primary planet pinion, secondary planetary gear or third-level planetary gear are made of at least two gears.
Compared to existing technology, the invention has the beneficial effects as follows:
The velocity ratio of gear drive outputs at different levels depends on the ratio between controlled certain one-level sun gear and the gear at different levels.The present invention is by the rotating speed of control sun gears 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, 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 can also increase level Four or the above gear drive of Pyatyi on the basis of tertiary gear driving mechanism, by controlling the rotation of sun gears at different levels, constitute step by-step variable gear and multistage output unit.
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 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 input shaft, output shaft.Planetary multilevel gear drive mechanism also comprises the planet carrier of fixedlying connected with the input shaft concentric, is located at planet axis on the planet carrier, is fixedly arranged on planetary gear set on the planet axis, is fixedly arranged on one-level sun gear on the output shaft, is located at secondary sun gear and three grades of sun gears on the described input shaft by means of bearing housing by means of bearing.Wherein, 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, also be installed with first flange of external connection on the secondary sun gear, first flange is located on the input shaft by means of bearing housing, three grades of sun gears are located on first flange by means of bearing housing, also be installed with second flange of external connection on three grades of sun gears, described second flange is located on first flange by means of bearing housing.
Embodiments of the invention one are referring to Fig. 1.
By control one-level sun gear 3, make between planet carrier 2 and the secondary sun gear 10 and between three grades of sun gears 9 and realize the speed change transmission.By control secondary sun gear 10, make between planet carrier 2 and the one-level sun gear 3 and between three grades of sun gears 9 and realize the speed change transmission.By controlling three grades of sun gears 9, make between planet carrier 2 and the one-level sun gear 3 and realization speed change transmission between the secondary sun gear 10.Whole control process is to be to control the ratio that realizes between certain one-level sun gear 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 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.
This structure can also increase level Four or the above gear drive of Pyatyi on the basis of tertiary gear driving mechanism, by controlling the rotation of sun gears at different levels, constitute step by-step variable gear and multistage output unit.
Embodiments of the invention two structures are referring to Fig. 2 and Fig. 4.
As accompanying drawing 2, Fig. 4 is planetary multilevel gear drive mechanism embodiment two of the present invention---the structural representation of resistance type stepless speed changes devices and controlling method.The rotating shaft of fixedly connected oil hydraulic pump 100 on three grades of connection method orchids 11 of above-mentioned planetary multilevel gear drive mechanism.The rotating shaft of oil hydraulic pump 100 is connected with secondary adpting flange 12 by bearing, and the shell of oil hydraulic pump 100 is fixedlyed connected with body 1.The rotating shaft of fixedly connected oil hydraulic pump 101 on the secondary adpting flange.The rotating shaft of oil hydraulic pump 101 is connected with input shaft 13 by bearing, and the shell of oil hydraulic pump 101 is fixedlyed connected with body 1.
The filler opening of oil hydraulic pump 100 is connected with the outlet of one-way valve a1, and the filler opening of oil hydraulic pump 101 is connected with the outlet of one-way valve a3.The inlet parallel of one-way valve a1 and one-way valve a3 and the hydraulic oil of fuel reserve tank are connected, and the oil outlet of oil hydraulic pump 100 is connected with pressure transducer c1 by a tee union.The control power supply of hydrostatic sensor c1 is connected with controller, and another interface on the tee union is connected with the filler opening of one-way valve a2.The oil outlet of oil hydraulic pump 101 also is connected with pressure transducer c2 by a tee union, and the control power supply of hydrostatic sensor c2 is connected with controller, and another interface on the tee union is connected with the filler opening of one-way valve a3.The oil outlet of one-way valve a2 is connected on the interface P of hydrovalve b1, the interface T sealing on the hydrovalve b1, and the oil outlet of one-way valve a3 is connected on the interface P of hydrovalve b2, the interface T sealing on the hydrovalve b2.Hydrovalve b1 is connected with the filler opening of cooling unit with the interface B on the hydrovalve b2 is in parallel.The oil outlet of cooling unit and fuel reserve tank are connected.Hydrovalve b1 is connected with the oil inlet P of hydraulic proportion valve with the interface A on the 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 shaft 13 drives planet carriers 2, 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 being subjected to the resistance of output shaft 4, the rotation of one-level sun gear 3 is controlled, transmission secondary sun gear 10 and three grades of sun gears 9 drive corresponding oil hydraulic pump 100 and oil hydraulic pump 101 rotations, and then not transmission between input shaft 13 and the output shaft 4 is in separated state.Controlled when in running order as hydrovalve b1, interface P on the hydrovalve b1 and interface A connect, and the oil outlet of oil hydraulic pump 100 is subjected to hydraulic proportion valve control, the flow of controller control hydraulic proportion valve.The rotating speed of oil hydraulic pump 100 is subjected to resistance (three grades of sun gears 9 when stationary state, with the velocity ratio of one-level sun gear 3 be negative).During resistance that the resistance that oil hydraulic pump 100 is subjected to is subjected to greater than output shaft 4, begin to realize transmission between three grades of sun gears 9 and the one-level sun gear 3, then same direction is rotated between output shaft 4 and the input shaft 13, and hydrovalve b2 is not controlled, begin to realize transmission equally between three grades of sun gears 9 and the secondary sun gear 10, and drive oil hydraulic pump 101 rotations 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 oil hydraulic pump 100 is subjected to is big more, its rotating speed step-down, and the rotating speed of output shaft 4 and oil hydraulic pump 101 then uprises, and the high more resistance that is subjected to relatively of output shaft 4 rotating speeds is big more, and the pressure that oil hydraulic pump 100 produces is also big more.If during the pressure that the resistance that is subjected to of output shaft 4 produces greater than oil hydraulic pump 100, the rotating speed of oil hydraulic pump 100 is corresponding to uprise, the relative step-down of rotating speed of output shaft 4 and oil hydraulic pump 101, pressure transducer c1 reaches controller with the pressure data of oil hydraulic pump 100, controller is followed the height according to required output shaft 4 rotating speeds, control the flow size of hydraulic proportion valve again, the rotation of control oil hydraulic pump 100 is subjected to corresponding resistance, makes the rotating speed of output shaft 4 or high or low.When if output shaft 4 rotating speeds are greater than the rotating speed of one-level sun gear 3 owing to coherence power, one-way valve a1 that is connected with oil outlet by oil hydraulic pump 100 filler openings and one-way valve a2 restriction oil hydraulic pump 100 can not backward rotation, make output shaft 4 rotating speeds be subjected to the restriction of input shaft 13 driving power device, realize unidirectional stepless change transmission between input shaft 13 and the output shaft 4.When hydrovalve b2 controlled when in running order, interface P on the hydrovalve b2 and interface A connect, the oil outlet of oil hydraulic pump 101 is subjected to hydraulic proportion valve control, the flow of controller control hydraulic proportion valve, the rotating speed of oil hydraulic pump 101 is subjected to resistance (two sun gears 10 when stationary state, with the velocity ratio of one-level sun gear 3 be positive number).During resistance that the resistance that oil hydraulic pump 101 is subjected to is subjected to greater than output shaft 4, begin to realize transmission between secondary sun gear 10 and the one-level sun gear 3, then opposite direction rotates between output shaft 4 and the input shaft 13, and hydrovalve b1 is not controlled, begin to realize transmission equally between secondary sun gear 10 and three grades of sun gears 9, and drive oil hydraulic pump 100 rotations 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 oil hydraulic pump 101 is subjected to is big more, its rotating speed step-down, and output shaft 4 and oil hydraulic pump 100 rotating speeds then uprise, and the high more resistance that is subjected to of output shaft 4 rotating speeds is big more, and the pressure that oil hydraulic pump 101 produces is also big more.If during the pressure that the resistance that is subjected to of output shaft 4 produces greater than oil hydraulic pump 101, the rotating speed of oil hydraulic pump 101 is corresponding to uprise, the relative step-down of rotating speed of output shaft 4 and oil hydraulic pump 100, pressure transducer c2 reaches controller with the pressure data of 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 control oil hydraulic pump 101 is subjected to corresponding resistance, makes the rotating speed of output shaft 4 or high or low.When if output shaft 4 rotating speeds are greater than the rotating speed of one-level sun gear 3 owing to coherence power, one-way valve a3 that is connected with oil outlet by oil hydraulic pump 101 filler openings and one-way valve a4 restriction oil hydraulic pump 101 can not backward rotation, make output shaft 4 rotating speeds be subjected to the restriction of input shaft 13 driving power device, realize rightabout stepless change transmission between input shaft 13 and the output shaft 4.The resistance size that this structure is subjected to by controlling two oil hydraulic pumps, the rotating speed of restriction secondary sun gear 10 and three grades of sun gears 9, 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 planetary multilevel gear drive mechanism embodiments three of the present invention---the structural representation of resistance type step change device.Fixedly connected three tier structure Moving plate 22 on three grades of connection method orchids 11 of above-mentioned planetary multilevel gear drive mechanism, along the corresponding three-stage brake device 201 of installing of three tier structure Moving plate 22 peripheries, fixedly connected two-stage system Moving plate 21 on secondary adpting flange 12, along the corresponding two stage braking device 200 of installing of three tier structure Moving plate 21 peripheries, constitute resistance type step change device.Or on the basis of tertiary gear driving mechanism, increasing level Four or the above gear drive of Pyatyi, and corresponding brake disc and the braking device installed controlled the rotation of sun gears at different levels by braking device, constitutes many gears of resistance type step change device.
Said structure, wherein, primary planet pinion 6, secondary planetary gear 7 can be a disjunctor gear.
Wherein, primary planet pinion 6, secondary planetary gear 7 and planet axis 5 can be as a whole.
Wherein, primary planet pinion 6, secondary planetary gear 7 and third-level planetary gear 8 can be a disjunctor gear.
Wherein, primary planet pinion 6, secondary planetary gear 7, third-level planetary gear 8 and planet axis 5 can be as a whole.
Wherein, one-level sun gear 3, output shaft 4 can be as a whole.
Wherein, secondary sun gear 10, secondary adpting flange 12 can be as a whole.
Wherein, three grades of sun gears 9, three grades of connection method orchids 11 can be as a whole.
Wherein, primary planet pinion, secondary planetary gear or third-level planetary gear are arranged and are constituted by one, two or more gears.
Wherein, primary planet pinion, secondary planetary gear or third-level planetary gear are arranged and are constituted by one, two or more gears.
Wherein, primary planet pinion, secondary planetary gear or third-level planetary gear are arranged and are constituted by one, two or more gears.
Claims (4)
1. planetary multilevel gear drive mechanism, comprise input shaft, output shaft, the planet carrier of fixedlying connected, be located at planet axis on the planet carrier, be fixedly arranged on planetary gear set on the planet axis, be fixedly arranged on the one-level sun gear on the output shaft that described planetary gear set comprises a primary planet pinion with the engagement of one-level sun gear by means of bearing with the input shaft concentric; It is characterized in that:
Described planetary multilevel gear drive mechanism also comprises by means of bearing housing is located at secondary sun gear and three grades of sun gears on the described input shaft; Wherein, described planetary gear set also comprises the secondary planetary gear and the third-level planetary gear that meshes with three grades of sun gears that mesh with secondary sun gear, also be installed with first flange of external connection on the described secondary sun gear, described first flange is located on the input shaft by means of bearing housing, described three grades of sun gears are located on first flange by means of bearing housing, also be installed with second flange of external connection on described three grades of sun gears, described second flange is located on first flange by means of bearing housing.
2. planetary multilevel gear drive mechanism according to claim 1 is characterized in that: described first flange, second flange connect oil hydraulic pump.
3. planetary multilevel gear drive mechanism according to claim 1 is characterized in that: described first flange, second flange connect brake disc.
4. according to claim 1 or 2 or 3 described planetary multilevel gear drive mechanisms, it is characterized in that: described primary planet pinion, secondary planetary gear or third-level planetary gear are made of at least two gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007101250470A CN101201096B (en) | 2007-12-17 | 2007-12-17 | Planetary multilevel gear drive mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007101250470A CN101201096B (en) | 2007-12-17 | 2007-12-17 | Planetary multilevel gear drive mechanism |
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| Publication Number | Publication Date |
|---|---|
| CN101201096A CN101201096A (en) | 2008-06-18 |
| CN101201096B true CN101201096B (en) | 2010-10-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101250470A Expired - Fee Related CN101201096B (en) | 2007-12-17 | 2007-12-17 | Planetary multilevel gear drive mechanism |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102635674A (en) * | 2012-05-17 | 2012-08-15 | 郭克亚 | Double-stage planet wheel continuously variable transmission mechanism |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101251174B (en) * | 2008-01-29 | 2010-11-17 | 郭克亚 | Planetary multilevel gear drive mechanism |
| CN103256352B (en) * | 2013-04-28 | 2015-08-19 | 河南科技大学 | Double planet wheel rows of mixing convergent current type many grades of multi-clutch speed changers |
| CN103277469B (en) * | 2013-04-28 | 2015-07-15 | 河南科技大学 | Planet busbar type multi-shaft clutch speed-changing device |
-
2007
- 2007-12-17 CN CN2007101250470A patent/CN101201096B/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102635674A (en) * | 2012-05-17 | 2012-08-15 | 郭克亚 | Double-stage planet wheel continuously variable transmission mechanism |
| CN102635674B (en) * | 2012-05-17 | 2014-10-22 | 郭克亚 | Double-stage planet wheel continuously variable transmission mechanism |
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| Publication number | Publication date |
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| CN101201096A (en) | 2008-06-18 |
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