CN204186894U - Balanced planetary gear buncher - Google Patents
Balanced planetary gear buncher Download PDFInfo
- Publication number
- CN204186894U CN204186894U CN201420407830.1U CN201420407830U CN204186894U CN 204186894 U CN204186894 U CN 204186894U CN 201420407830 U CN201420407830 U CN 201420407830U CN 204186894 U CN204186894 U CN 204186894U
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- CN
- China
- Prior art keywords
- planetary gear
- cylindrical
- gear
- gearings
- cone
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Abstract
The balanced planetary gear buncher that the utility model provides, belongs to transmission technology field, mainly solves the problem that prior art has pole speed changer cost height complex structure, buncher line belt to skid.Comprise input shaft, jack shaft, output shaft, cone planetary train of gearings, cylindrical planetary train of gearings, cylindrical planetary gear carrier, balance gear, damping device and bearing, be characterized in: described cone planetary train of gearings is connected with described cylindrical planetary train of gearings by jack shaft, again by regulating rotating speed and the sense of rotation of described balance gear or cylindrical planetary gear carrier, and then reach the object of speed change.The utility model transmission efficiency is high, bearing torque is large, speed change is steady, the simple efficiency of structure is high, without skidding.
Description
Technical field
The utility model belongs to transmission technology field, is specifically related to balanced planetary gear buncher.
Background technique
In present transmission device, speed changer uses direct shift transmission (DSG) and stepless speed variator (CVT).DSG advantage is that gear-driven efficiency is high, bearing torque is large, speed change is steady, and shortcoming is that complex structure cost is high, belongs to multi-change speed.The advantage of CVT achieves electrodeless variable-speed, and the simple efficiency of structure is high.Shortcoming be moment of torsion large time transmit with skidding.
Summary of the invention
Problem to be solved in the utility model realizes stepless change and moment of torsion is non-slip greatly, provides balanced planetary gear buncher.
The utility model is solve the problems of the technologies described above the technological scheme taked to be:
Balanced planetary gear buncher, comprises input shaft, jack shaft, output shaft, cone planetary train of gearings, cylindrical planetary train of gearings, cylindrical planetary gear carrier and bearing, is characterized in:
Described cone planetary train of gearings is connected by cylindrical planetary gear carrier and jack shaft with cylindrical planetary train of gearings, wherein cylindrical planetary gear carrier can be controlled by external force in transmission process, can the speed discrepancy of control inputs axle and output shaft by controlling the rotational velocity of cylindrical planetary gear carrier and sense of rotation.
Described cone planetary train of gearings comprises cone planetary gear stand, the longitudinal axis, the first taper sun gear, the second taper sun gear, the first cone planetary gear, the second cone planetary gear, taper sun gear ring; Be slidably connected with input shaft in the middle part of described cone planetary gear stand, its two ends and the described longitudinal axis are slidably connected; Described first taper sun gear is connected with described input shaft, with the first cone planetary gears meshing; Described second cone planetary gear is connected with the first cone planetary gear parallel coaxial by the longitudinal axis; Described taper sun gear ring and the second cone planetary gears meshing, and be connected with cylindrical planetary gear carrier; Described second taper sun gear is connected with the cylindrical sun gear in cylindrical planetary train of gearings by described jack shaft;
Described cylindrical planetary train of gearings comprises cylindrical planetary gear carrier, the cylindrical sun gear of internal tooth, cylindrical planetary gear and cylindrical sun gear; Described cylindrical planetary gear carrier is connected with taper sun gear ring; Described cylindrical planetary gear engages with cylindrical sun gear; Described internal tooth sun gear and cylindrical planetary gears meshing, be connected with output shaft in the middle part of it;
Described bearing comprises the input shaft bearing being positioned at transmission input and the output shaft bearing being positioned at transmission output;
Described input shaft is connected with input shaft bearing sliding; Described output shaft is connected with output shaft bearing sliding; Described jack shaft one end and input shaft are slidably connected by connection set, and the other end and output shaft are slidably connected by connection set;
Also comprise balance gear and damping device, middle part and the jack shaft of described balance gear are slidably connected, and are connected with cylindrical planetary gear carrier;
Described damping device input end is connected to damping gear, and described damping gear engages with described balance gear.
Described damping device is gear pump arrangement or variable speed electric motors, particularly.
The utility model compared with prior art, has following beneficial effect:
The utility model adopts cone planetary train of gearings, cylindrical planetary train of gearings, balance gear, jack shaft and damping device, by rotating speed and the sense of rotation of damping device or variable speed electric motors, particularly adjustment gear or cylindrical planetary gear carrier, thus realize stepless change, transmission efficiency is high, bearing torque is large, speed change is steady, the simple efficiency of structure is high, without skidding.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model.
In figure: 1-input shaft; 2-the first taper sun gear; 3-the first cone planetary gear; 4-the second cone planetary gear; 5-taper sun gear ring; 6-balance gear; 7-the second taper sun gear; 8-connection set; 9-cylindrical planetary gear carrier; The cylindrical sun gear of 10-internal tooth; 11-cylindrical planetary gear; 12-output shaft bearing; 13-output shaft; 14-cylindrical sun gear; 15-jack shaft; 16-damping device; 17-damping gear; 18-longitudinal axis; 19-cone planetary gear stand; 20-input shaft bearing.
Embodiment
As shown in Figure 1, balanced planetary gear buncher, comprises input shaft 1, jack shaft 15, output shaft 13, cone planetary train of gearings, cylindrical planetary train of gearings, cylindrical planetary gear carrier 9 and bearing;
Described cone planetary train of gearings is connected by cylindrical planetary gear carrier 9 and jack shaft 15 with cylindrical planetary train of gearings, wherein cylindrical planetary gear carrier 9 can be controlled by external force in transmission process, can the speed discrepancy of control inputs axle 1 and output shaft 13 by controlling the rotational velocity of cylindrical planetary gear carrier 9 and sense of rotation.
Described cone planetary train of gearings comprises cone planetary gear stand 19, the longitudinal axis 18, first taper sun gear 2, second taper sun gear 7, first cone planetary gear 3, second cone planetary gear 4, taper sun gear ring 5; Be slidably connected with input shaft 1 in the middle part of described cone planetary gear stand 19, its two ends and the described longitudinal axis 18 are slidably connected; Described first taper sun gear 2 is connected with described input shaft 1, engages with the first cone planetary gear 3; Described second cone planetary gear 4 is connected with the first cone planetary gear 3 parallel coaxial by the longitudinal axis 18; Described taper sun gear ring 5 engages with the second cone planetary gear 4, and is connected with cylindrical planetary gear carrier 9; Described second taper sun gear 7 is connected with the cylindrical sun gear 14 in cylindrical planetary train of gearings by described jack shaft 15;
Described cylindrical planetary train of gearings comprises cylindrical planetary gear carrier 9, the cylindrical sun gear of internal tooth 10, cylindrical planetary gear 11 and cylindrical sun gear 14; Described cylindrical planetary gear carrier 9 is connected with taper sun gear ring 5; Described cylindrical planetary gear 11 engages with cylindrical sun gear 14; Described internal tooth sun gear 10 engages with cylindrical planetary gear 11, is connected in the middle part of it with output shaft 13;
Described bearing comprises the input shaft bearing 20 being positioned at transmission input and the output shaft bearing 12 being positioned at transmission output;
Described input shaft 1 is slidably connected with input shaft bearing 20; Described output shaft 13 is slidably connected with output shaft bearing 12; Described jack shaft 15 one end and input shaft 1 are slidably connected by connection set 8, and the other end and output shaft 13 are slidably connected by connection set 8;
Also comprise balance gear 6 and damping device 16, middle part and the jack shaft 15 of described balance gear 6 are slidably connected, and are connected with cylindrical planetary gear carrier 9;
Described damping device 16 input end is connected to damping gear 17, and described damping gear 17 engages with described balance gear 6.
Described damping device 16 is gear pump arrangement or variable speed electric motors, particularly.
Working principle:
During work, input shaft 1 drives the first taper sun gear 2 postive direction to rotate, and the first taper sun gear 2 drives the first cone planetary gear 3 and the second cone planetary gear 4 to rotate.Now, suppose that taper sun gear ring 5 does not rotate.While first cone planetary gear 3 and the second cone planetary gear 4 rotation, postive direction revolves round the sun and drives the second taper sun gear 7 to reverse, and gives the taper sun gear ring power that 5 one postive directions are rotated simultaneously.Second taper sun gear 7 drives cylindrical sun gear 14 counter-rotation.Cylindrical sun gear 14 drives cylindrical planetary gear 11 to rotate, and gives the power of cylindrical planetary gear carrier 9 one counter-rotation simultaneously.The power of now taper sun gear ring 5 postive direction rotation and the contrary equal and opposite in direction of force direction of cylindrical planetary gear carrier 9 counter-rotation, thus form balance.So make cylindrical planetary gear carrier 9 and taper sun gear ring 5 not rotate.Cylindrical sun gear 14 changes sense of rotation by cylindrical planetary gear 11 and drives internal tooth sun gear 10 rotate forward and slow down, then exports the power of low rotation speed large torque by output shaft 13.If the cylindrical planetary gear carrier now on equinoctial point 9 and taper sun gear ring 5 postive direction are rotated and speed change just can make output shaft 13 realize speed change.Because the frictional force between gear can make cylindrical planetary gear carrier on equinoctial point 9 and taper sun gear ring 5 postive direction rotate thus cause speed changer can not speed change in real work.So need the rotating speed of manual control cylindrical planetary gear carrier 9 and taper sun gear ring 5 thus realize electrodeless variable-speed.
The power that cylindrical planetary gear carrier 9 postive direction can be utilized to rotate makes it engage drive damping device 16 by balance gear 6 with damping gear 17, by controlling the rotating speed of the resistance switch control rule cylindrical planetary gear carrier 9 of damping device 16 thus realizing speed change.
Can the rotating speed of cylindrical planetary gear carrier 9 be controlled by variable speed electric motors, particularly thus realize speed change.Motor can also make cylindrical planetary gear carrier 9 reverse thus output shaft 13 is not rotated, and realizes the function of clutch.
Because the fluctuation of power can make equinoctial point unstable in straight-tooth gear transmission process, make cylindrical planetary gear carrier 9 and taper sun gear ring 5 occur reversal phenomenon, increase the difficulty controlling its rotating speed.So all gears of this device all need to use angular gear thus the stability improving equinoctial point.
The left side that in Fig. 1, taper sun gear ring 5 is arranged on cone planetary gear 3 and 4 also can realize this function.
Claims (2)
1. balanced planetary gear buncher, comprises input shaft (1), jack shaft (15), output shaft (13), cone planetary train of gearings, cylindrical planetary train of gearings, cylindrical planetary gear carrier (9) and bearing; It is characterized in that:
Also comprise balance gear (6) and damping device (16), middle part and the jack shaft (15) of described balance gear (6) are slidably connected, and are connected with cylindrical planetary gear carrier (9); Described damping device (16) input end is connected to damping gear (17), and described damping gear (17) engages with described balance gear (6);
Described cone planetary train of gearings is connected by cylindrical planetary gear carrier (9) and jack shaft (15) with cylindrical planetary train of gearings, wherein cylindrical planetary gear carrier (9) can be controlled by external force in transmission process, can the speed discrepancy of control inputs axle (1) and output shaft (13) by controlling the rotational velocity of cylindrical planetary gear carrier (9) and sense of rotation.
2. balanced planetary gear buncher according to claim 1, is characterized in that: described cone planetary train of gearings comprises cone planetary gear stand (19), the longitudinal axis (18), the first taper sun gear (2), the second taper sun gear (7), the first cone planetary gear (3), the second cone planetary gear (4), taper sun gear ring (5); Described cone planetary gear stand (19) middle part is slidably connected with input shaft (1), and its two ends and the described longitudinal axis (18) are slidably connected; Described first taper sun gear (2) is connected with described input shaft (1), engages with the first cone planetary gear (3); Described second cone planetary gear (4) is connected with the first cone planetary gear (3) parallel coaxial by the longitudinal axis (18); Described taper sun gear ring (5) is engaged with the second cone planetary gear (4), and is connected with cylindrical planetary gear carrier (9); Described second taper sun gear (7) is connected with the cylindrical sun gear (14) in cylindrical planetary train of gearings by described jack shaft (15);
Described cylindrical planetary train of gearings comprises cylindrical planetary gear carrier (9), the cylindrical sun gear of internal tooth (10), cylindrical planetary gear (11) and cylindrical sun gear (14); Described cylindrical planetary gear carrier (9) one end is connected with taper sun gear ring (5), and the other end is as the axis of rotation of cylindrical planetary gear (11); Described cylindrical planetary gear (11) is engaged with cylindrical sun gear (14); Described internal tooth sun gear (10) is engaged with cylindrical planetary gear (11), is connected in the middle part of it with output shaft (13);
Described bearing comprises the input shaft bearing (20) being positioned at transmission input and the output shaft bearing (12) being positioned at transmission output;
Described input shaft (1) and input shaft bearing (20) are slidably connected; Described output shaft (13) and output shaft bearing (12) are slidably connected; Described jack shaft (15) one end and input shaft (1) are slidably connected by connection set (8), and the other end and output shaft (13) are slidably connected by connection set (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420407830.1U CN204186894U (en) | 2014-07-23 | 2014-07-23 | Balanced planetary gear buncher |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420407830.1U CN204186894U (en) | 2014-07-23 | 2014-07-23 | Balanced planetary gear buncher |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204186894U true CN204186894U (en) | 2015-03-04 |
Family
ID=52618901
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420407830.1U Expired - Fee Related CN204186894U (en) | 2014-07-23 | 2014-07-23 | Balanced planetary gear buncher |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204186894U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104728369A (en) * | 2015-03-20 | 2015-06-24 | 杨晋杰 | Balanced type infinitely variable transmission |
| CN104847853A (en) * | 2015-05-18 | 2015-08-19 | 杨晋杰 | Gear type self-adapting transmission |
| CN105134892A (en) * | 2015-06-17 | 2015-12-09 | 杨晋杰 | Asymmetric gear type self-adaptation speed changer |
-
2014
- 2014-07-23 CN CN201420407830.1U patent/CN204186894U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104728369A (en) * | 2015-03-20 | 2015-06-24 | 杨晋杰 | Balanced type infinitely variable transmission |
| CN104847853A (en) * | 2015-05-18 | 2015-08-19 | 杨晋杰 | Gear type self-adapting transmission |
| CN105134892A (en) * | 2015-06-17 | 2015-12-09 | 杨晋杰 | Asymmetric gear type self-adaptation speed changer |
| CN105134892B (en) * | 2015-06-17 | 2017-11-14 | 山西能源学院 | Unsymmetric gear formula adaptive transmission |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150304 Termination date: 20150723 |
|
| EXPY | Termination of patent right or utility model |