CN210600053U - Centrifugal force automatic transmission - Google Patents
Centrifugal force automatic transmission Download PDFInfo
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- CN210600053U CN210600053U CN201920519351.1U CN201920519351U CN210600053U CN 210600053 U CN210600053 U CN 210600053U CN 201920519351 U CN201920519351 U CN 201920519351U CN 210600053 U CN210600053 U CN 210600053U
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Abstract
The utility model provides a centrifugal force automatic gearbox relates to derailleur technical field, include the shell body, locate derailleur power input shaft and derailleur power output shaft in the shell body and in speed change mechanism between derailleur power input shaft and the derailleur power output shaft, this speed change mechanism includes: the planetary gear set comprises a centrifugal force reducing planetary carrier, a first group of planetary gears, a second group of planetary gear sets and a third group of planetary output wheels. The utility model has the advantages that: the mechanical two-stage automatic speed change is realized by adjusting the rotating speed and the torque output under the condition of different linear speeds through the centrifugal variable-diameter planet carrier, and similarly, after the two-stage deformer is assembled in a multi-stage series mode, the multi-stage speed change can be realized, so that the advantages of small structure, low cost, high operation reliability, direct transmission efficiency and the like are achieved, and the mechanical two-stage automatic speed change device is particularly suitable for the low-speed and high-torque characteristics of the motor of an electric automobile.
Description
Technical Field
The utility model relates to a derailleur technical field especially relates to a novel can carry out centrifugal force automatic gearbox of multistage series connection with second grade variable speed.
Background
A transmission is a mechanism for changing the speed and torque from an engine that can change the output and input shaft gear ratios, either fixed or in steps. The speed variator consists of speed-changing transmission mechanism and control mechanism, and some vehicles also have power output mechanism. The transmission mechanism is mainly driven by common gears and also driven by planetary gears.
The variation mode of the transmission ratio is divided into: the method comprises three types of step type, stepless type and comprehensive type. The step-type transmission has several selectable fixed transmission ratios and adopts gear transmission; can be divided into: a common gear transmission with a fixed gear axis and a planetary gear transmission with a part gear (planetary gear) axis rotating.
The motor of the existing electric automobile is not suitable for being configured with a transmission due to overlarge kinetic energy loss of the motor caused by overlarge volume of the traditional transmission, but the existing electric automobile has the defects of low power consumption during low-speed running and great increase of the power consumption during high-speed running, the speed regulation is realized by singly changing the changes of input current, voltage and frequency, and the low-speed high-torque characteristic of the motor is still not exerted so far.
In order to solve the prior art not enough, the utility model provides a small and exquisite light, low cost, operation and the simple centrifugal force automatic gearbox of installation make the advantage of electric automobile low-speed high torsion play continuously, and the high-speed high power consumptive drawback is solved.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a can carry out multistage centrifugal force automatic gearbox who establishes ties with the second grade variable speed.
The utility model provides a pair of centrifugal force automatic gearbox, include the shell body, locate derailleur power input shaft and derailleur power output shaft in the shell body and in speed change mechanism between derailleur power input shaft and the derailleur power output shaft, this speed change mechanism includes: the centrifugal force reducing planet carrier is arranged on the power input shaft of the speed changer and keeps rotating at the same angular speed with the power input shaft of the speed changer;
the group A of planet gears comprise a sun gear fixed on the power input shaft of the transmission, a planet gear A meshed with the sun gear, an inner and outer double-gear-surface outer gear ring and a double-gear-surface inner gear ring meshed with the planet gear A;
the planetary gear set B comprises at least one gear set formed by at least one pair of planetary gears B, the planetary gear set B is limited to penetrate through a sleeve in the centrifugal force reducing planetary carrier and rotates at the same angular speed along the centrifugal force reducing planetary carrier and the power input shaft of the transmission;
the sun gear in the planetary gear set B borrows the inner and outer double-gear-surface outer gear rings, and the outer gear ring of the planetary gear set B borrows the inner and outer double-gear-surface inner gear rings;
and the third group of planet output wheels are composed of planet wheels and a basin gear ring with an arc tooth surface, and the basin gear ring and the transmission power output shaft are fixed into an integrated structure.
The centrifugal force reducing planet carrier comprises a central seat ring arranged on the power input shaft of the speed changer, a parallel double-connecting-rod mechanism provided with a hinge joint, a sleeve and a tension spring; the central seat ring is connected with one end of the parallel double-link mechanism through the hinge, and the other end of the parallel double-link mechanism is connected with the sleeve for supporting a group of coaxial planet wheels through the hinge; the central seat ring and the sleeve are also tensioned through the tensioning spring.
The planet gear A is designed for a large and small step type double-tooth structure and is arranged on the outer shell through a fixing shaft. The small tooth part of the planet gear A is meshed with the inner and outer double-tooth-surface outer gear rings, and the large tooth part of the planet gear A is meshed with the inner gear ring of the double-tooth-surface.
The gear set consists of a group of input planet gears B and an output planet gear B which rotate reversely;
the utility model discloses a theory of operation is:
along with the rotation angular speed of the second group of planet gears which penetrate through the sleeve in the centrifugal force reducing planet carrier is higher and higher, the centrifugal force applied to the centrifugal force reducing planet carrier for bearing the second group of planet gears is larger and larger, when the centrifugal force is large enough to overcome the spring tension, the second group of planet gears do arc motion under the directional constraint of the centrifugal force reducing planet carrier, leave the inner and outer double-gear-plane outer gear rings of the first group of planet gears and cut into the inner gear ring of the double-gear-plane of the first group of planet gears. The outer gear ring of the inner and outer double-tooth surfaces of the planet gear set A and the inner gear ring of the double-tooth surfaces of the planet gear set A are connected in series through the planet gear set A which is designed into a big and small step double-tooth structure and rotate in the same direction. In the second group of planet gears, a group of input gear sets rotating in opposite directions are arranged on the inner and outer double-gear-surface outer gear rings and the inner double-gear-surface inner gear rings of the first group of planet gears, and the motion switching is carried out under the directional constraint of the centrifugal force reducing planet carrier, so that the input of different gear linear speeds of the second group of planet gears is realized. The output gear in the planet gear group B is the input gear (namely planet gear C) of the planet output gear group C, the planet gear C is used as the power input gear of the planet output gear group C, the inner circular arc slides in the basin gear ring of the planet output gear group C, and the rotation speed and the torque are transmitted in a rotating mode, so that the output speed and the torque of the whole speed changer are driven.
The inner and outer double-tooth-surface outer gear rings and the inner gear rings of the first group of planet gears are driven by the first planet gear to realize differential rotation, so that the problem of low-impact meshing of the second group of planet gears in dynamic connection is effectively solved, and the meshing is more flexible. If necessary, in order to further reduce the impact, a meshing synchronizer can be arranged on the planet wheel of the second group.
An output gear (namely a planet gear C) on the planet gear of the second group is always meshed with the basin teeth of the planet output gear of the third group, so that the planet output gear always has an angular speed state in a normal running state, and the meshing process of dynamic connection and dynamic connection is ensured.
When the external carrier limits power (such as an automobile brake state), the centrifugal force variable planet carrier does not have the angular speed of the input shaft, so that the centrifugal force does not exist or the centrifugal force is rapidly reduced, and under the tension force of the spring, the group B planet gears return to the inner and outer tooth ring outside the inner and outer tooth ring from the inner tooth ring of the group A planet gears, so that low-speed forward or reverse operation is realized.
The utility model has the advantages that: the mechanical two-stage automatic speed change is realized by adjusting the rotating speed and the torque output under the condition of different linear speeds through the centrifugal variable-diameter planet carrier, and similarly, after the two-stage deformer is assembled in a multi-stage series mode, the multi-stage speed change can be realized, so that the advantages of small structure, low cost, high operation reliability, direct transmission efficiency and the like are achieved, and the mechanical two-stage automatic speed change device is particularly suitable for the low-speed and high-torque characteristics of the motor of an electric automobile.
Drawings
FIG. 1 is a schematic view of the overall cross-sectional structure of the present invention;
fig. 2 is a schematic cross-sectional view of the entire transmission mechanism 4 of the present invention;
fig. 3 is another schematic sectional view of the whole transmission mechanism 4 according to the present invention;
fig. 4 is a schematic cross-sectional structure diagram of the centrifugal force reducing planet carrier 41 of the present invention;
fig. 5 is a schematic cross-sectional view of the first group planetary gear 42 according to the present invention;
fig. 6 is a schematic sectional view of the second planetary gear set 43 of the present invention;
fig. 7 is a schematic sectional view of the planetary output wheel 44 of the third group of the present invention.
Detailed Description
The present invention will be described in detail with reference to the following embodiments and accompanying drawings. It should be noted that the description of the embodiments is provided to help understanding of the present invention, but the present invention is not limited thereto. In addition, the technical features related to the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other. In addition, the following are only some embodiments, not all embodiments, and all other embodiments obtained by a person of ordinary skill in the art without creative efforts based on the embodiments of the present invention belong to the protection scope of the present invention.
Example 1
Referring to fig. 1-7, a centrifugal force automatic transmission includes an outer casing 1, a transmission power input shaft 2 and a transmission power output shaft 3 are installed in the outer casing 1, and a speed change mechanism 4 is installed between the transmission power input shaft 2 and the transmission power output shaft 3, the speed change mechanism 4 includes a centrifugal force reducing planet carrier 41, an a group planet wheel 42, a b group planet wheel set 43, and a c group planet output wheel 44, wherein:
the centrifugal force reducing carrier 41 (see fig. 4) is attached to the transmission power input shaft 2 and rotates at the same angular velocity as the transmission power input shaft 2. The centrifugal force reducing planet carrier 41 comprises a central race 411 arranged on the power input shaft 2 of the transmission, a parallel double-link mechanism 413 with one end connected with the central race 411 through a hinge joint 412, a sleeve 414 connected with the other end of the parallel double-link mechanism 413 through the hinge joint 412 and used for supporting a group of coaxial planet wheels, and a tension spring 415 used for tensioning the central race 411 and the sleeve 414;
the first group of planetary gears 42 (see fig. 5) includes a sun gear 421 fixed to the transmission power input shaft 2, a first planet gear 422 meshed with the sun gear 421, and an outer inner and outer double-gear-surface outer ring gear 423 and an inner double-gear-surface inner ring gear 424 meshed with the first planet gear 422, wherein the first planet gear 422 is designed to be a large and small stepped double-gear structure, and is provided on the outer casing 1 through a fixed shaft 5. The small tooth part of the planet gear A422 is meshed with the inner and outer double-tooth-plane outer gear ring 423, and the large tooth part of the planet gear A422 is meshed with the double-tooth-plane inner gear ring 424;
the group b planetary gear set 43 (see fig. 6) includes at least one gear set 430, where the gear set 430 is composed of at least one pair of planetary gears b 431, and the planetary gears b 431 are limitedly inserted into the sleeve 414 of the centrifugal reducing planetary carrier 41 and rotate at the same angular speed with the centrifugal reducing planetary carrier 41 and the transmission power input shaft 2; any one gear set 430 is composed of a set of input planet gear B431 'and an output planet gear B431' which rotate reversely, a sun gear in the planet gear set B43 borrows an inner and outer double-gear outer ring gear 423, and an outer ring gear of the planet gear set B43 borrows the inner and outer double-gear inner ring gear 424;
the group c planetary output wheel 44 (see fig. 7) is composed of a planetary wheel c 441 (i.e., an output planetary wheel b 431, which is indicated as 431 in the drawing) and a ring gear 442 with an arc tooth surface, and the ring gear 442 and the transmission power output shaft 3 are fixed into an integrated structure.
The utility model discloses a theory of operation is:
with the increasing rotation angular speed of the planet gear group b 431 in the planet gear group b 43 penetrating through the transmission power input shaft 2, the centrifugal force applied to the centrifugal force reducing planet carrier 41 for bearing the planet gear group b 43 is increased, and when the centrifugal force is large enough to overcome the spring tension, the planet gear group b 431 in the planet gear group b 43 performs arc motion under the directional constraint of the centrifugal force reducing planet carrier 41, leaves the inner and outer double-gear-face outer ring gear 423 in the planet gear group a 42, and cuts into the double-gear-face inner ring gear 424 in the planet gear group a 42. The inner and outer double-tooth-surface outer gear rings 423 and the double-tooth-surface inner gear ring 424 in the first group of planetary gears 42 are connected in series through a planetary gear a 422 designed in a large and small stepped double-tooth structure and rotate in the same direction. In the second planetary gear set 43, a gear set 430 composed of a set of input planetary gear second 431' and output planetary gear second 431 ″ rotating in opposite directions performs motion switching in the inner and outer double-tooth-surface outer ring gear 423 and the double-tooth-surface inner ring gear 424 in the first planetary gear set 42 by virtue of the directional constraint force of the centrifugal force reducing planet carrier 41, so that different gear linear velocities of the second planetary gear set 43 are input. The output planet gear 431 ″ of the planet gear set b 43 is the input gear (i.e., the planet gear 441) of the planet output gear set c 44, and the planet gear 441 is used as the power input gear of the planet output gear set c 44, slides in an arc manner in the ring gear 442 of the planet output gear set c 44, and rotates to transmit the rotating speed and the torque, so as to drive the output rotating speed and the torque of the whole transmission.
The inner and outer double-tooth-surface outer gear rings 423 and the inner and outer double-tooth-surface inner gear rings 424 of the group A planetary gear 42 are driven by the planetary gear A422 together to realize differential rotation, so that the problem of low-impact meshing of the input planetary gear B431 'and the output planetary gear B431' in the group B planetary gear set 43 and the dynamic connection between the inner and outer double-tooth-surface outer gear rings 423 and the inner and outer double-tooth-surface inner gear rings 424 is effectively solved, and the meshing is more flexible. If desired, to further reduce shock, a meshing synchronizer may be provided on the set B planetary gear set 43.
The output planet gear 431' on the planet gear set B43 is the input gear (i.e. planet gear C441) in the planet output gear set C44 and the basin ring gear 442 in the planet output gear set C44 are always meshed, so that the planet output gear set C has an angular speed state in a normal driving state, and the meshing process of the dynamic connection and the dynamic connection is ensured.
When the external carrier limits the power (for example, in a braking state of the automobile), the centrifugal force variable planet carrier 41 does not have the angular speed of the power input shaft 2 of the transmission, so that the centrifugal force or the rapid reduction of the centrifugal force does not exist, and under the tension of the spring, the planet gear 431 in the planet gear set B43 returns to the inner and outer double-gear-surface outer ring gears 423 from the double-gear-surface inner ring gear 424 of the planet gear set A42, so that the low-speed forward or reverse operation is realized.
The utility model has the advantages that: the rotating speed and the torque output under the condition of different linear speeds are adjusted through the centrifugal variable-diameter planet carrier 41, the mechanical two-stage automatic speed change is realized, and similarly, after the two-stage deformer is assembled in a multi-stage series mode, the multi-stage speed change can be realized, so that the advantages of small structure, low cost, high operation reliability, direct transmission efficiency and the like are achieved, and the motor low-speed high-torque transmission device is particularly suitable for the motor low-speed high-torque characteristics of an electric automobile.
Claims (6)
1. Centrifugal force automatic transmission, including the shell body, locate derailleur power input shaft and derailleur power output shaft in the shell body and between the speed change mechanism between derailleur power input shaft and the derailleur power output shaft, its characterized in that: the speed change mechanism includes:
the centrifugal force reducing planet carrier is arranged on the power input shaft of the speed changer and keeps rotating at the same angular speed with the power input shaft of the speed changer;
the group A of planet gears comprise a sun gear arranged on the power input shaft of the transmission, a planet gear A meshed with the sun gear, an inner and outer double-gear-surface outer gear ring and a double-gear-surface inner gear ring meshed with the planet gear A;
the planetary gear set B comprises at least one gear set formed by at least one pair of planetary gears B, and the planetary gear set B is limited to penetrate through a sleeve in the centrifugal force reducing planetary carrier and rotates at the same angular speed along with the centrifugal force reducing planetary carrier and the power input shaft of the transmission;
the third group of planet output wheels comprise planet wheels and a basin gear ring with an arc tooth surface, and the basin gear ring and the transmission power output shaft are fixed into an integrated structure.
2. The centrifugal force automatic transmission according to claim 1, characterized in that: and the sun gear in the second planetary gear set borrows the inner and outer double-gear-surface outer gear rings, and the outer gear ring of the second planetary gear set borrows the inner and outer double-gear-surface inner gear rings.
3. The centrifugal force automatic transmission according to claim 1, characterized in that: the centrifugal force reducing planet carrier comprises a central seat ring arranged on the power input shaft of the speed changer, a parallel double-connecting-rod mechanism provided with hinges, a sleeve and a tension spring.
4. The centrifugal force automatic transmission according to claim 1, characterized in that: the planet gear A is designed into a large and small step type double-tooth structure and is arranged on the outer shell through a fixed shaft;
the small tooth part of the planet gear A is meshed with the inner and outer double-tooth-surface outer gear rings, and the large tooth part of the planet gear A is meshed with the inner gear ring of the double-tooth-surface.
5. The centrifugal force automatic transmission according to claim 1, characterized in that: the gear set consists of a group of input planet gears B and output planet gears B which rotate reversely.
6. The centrifugal force automatic transmission according to claim 3, characterized in that: the central seat ring is connected with one end of the parallel double-link mechanism through the hinge, and the other end of the parallel double-link mechanism is connected with the sleeve for supporting a group of coaxial planet wheels through the hinge;
the central seat ring and the sleeve are also tensioned through the tensioning spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920519351.1U CN210600053U (en) | 2019-04-17 | 2019-04-17 | Centrifugal force automatic transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920519351.1U CN210600053U (en) | 2019-04-17 | 2019-04-17 | Centrifugal force automatic transmission |
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| CN210600053U true CN210600053U (en) | 2020-05-22 |
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| CN201920519351.1U Active CN210600053U (en) | 2019-04-17 | 2019-04-17 | Centrifugal force automatic transmission |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110030340A (en) * | 2019-04-17 | 2019-07-19 | 王世峰 | Centrifugal force automatic transmission |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110030340A (en) * | 2019-04-17 | 2019-07-19 | 王世峰 | Centrifugal force automatic transmission |
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