CN113803425B - Planetary speed change mechanism with large order ratio - Google Patents
Planetary speed change mechanism with large order ratio Download PDFInfo
- Publication number
- CN113803425B CN113803425B CN202110999885.0A CN202110999885A CN113803425B CN 113803425 B CN113803425 B CN 113803425B CN 202110999885 A CN202110999885 A CN 202110999885A CN 113803425 B CN113803425 B CN 113803425B
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- Prior art keywords
- gear
- brake
- planetary
- ratio
- sun gear
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- 230000007246 mechanism Effects 0.000 title claims abstract description 18
- 230000008859 change Effects 0.000 title abstract description 6
- 230000005540 biological transmission Effects 0.000 claims abstract description 29
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/02—Selector apparatus
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
Abstract
The invention discloses a large-order-ratio planetary speed change mechanism, which comprises a first planetary row, a second planetary row, a third planetary row, a first brake, a second brake, a third brake and a clutch, wherein the first brake is connected with the first planetary row; the first planetary row is an inner-outer meshing double-planetary row and comprises a first sun gear, a first gear ring and a first planet carrier; the second planetary row is an inner-outer meshing single-planetary row and comprises a second sun gear, a second gear ring and a second planet carrier; the third planetary row is an inner-outer meshing double-planetary row and comprises a third sun gear, a third gear ring and a third planetary carrier; a clutch is connected between the third sun gear and the third planet carrier; the first planet carrier is connected with the second sun gear or the second sun gear and the third gear ring; the first gear ring is connected with the second planet carrier and the third sun gear or the second planet carrier, and the invention has the advantages of large step ratio, compact structure, large bearing capacity and higher transmission efficiency.
Description
Technical Field
The invention relates to the technical field of planetary variable transmission, in particular to a large-order-ratio planetary variable transmission mechanism.
Background
Electrically driven vehicles require a transmission having a large step ratio to meet the output speed and torque demands, and existing planetary gear sets have difficulty achieving large gear ratios, large step ratios, within a suitable k-value (ratio of ring gear tooth number to sun gear tooth number).
Disclosure of Invention
In order to overcome the defects in the prior art, the invention provides a large-order-ratio planetary speed change mechanism to solve the problems in the prior art.
The technical scheme adopted for solving the technical problems is as follows: a large-order-ratio planetary speed change mechanism comprises a first planetary row, a second planetary row, a third planetary row, a first brake, a second brake, a third brake and a clutch;
the first planetary row is an inner-outer meshing double-planetary row and comprises a first sun gear, a first gear ring and a first planet carrier;
the second planetary row is an inner-outer meshing single-planetary row and comprises a second sun gear, a second gear ring and a second planet carrier;
the third planetary row is an inner-outer meshing double-planetary row and comprises a third sun gear, a third gear ring and a third planetary carrier;
a clutch is connected between the third sun gear and the third planet carrier;
the first planet carrier is connected with the second sun gear or the second sun gear and the third gear ring; the first gear ring is connected with the second planet carrier, the third sun gear or the second planet carrier.
Preferably, the clutch is a mechanical shifting element, a hydraulic shifting element or a pneumatic shifting element.
Preferably, the first planet carrier is an input end, the third gear ring is an output end, or the third sun gear is an input end, and the second planet carrier is an output end.
Preferably, the first brake, the second brake and the third brake are mechanical shifting elements, hydraulic shifting elements or pneumatic shifting elements, the first brake is used for braking the first sun gear, the second brake is used for braking the second gear ring, and the third brake is used for braking the third planet carrier.
Preferably, the first gear is achieved when the second brake and the third brake are engaged and the first brake and the clutch are disengaged, the second gear is achieved when the second brake and the clutch are engaged and the first brake and the third brake are disengaged, the third gear is achieved when the first brake and the third brake are engaged and the second brake and the clutch are disengaged, and the fourth gear is achieved when the first brake and the clutch are engaged and the second brake and the third brake are disengaged.
Preferably, the first gear has a gear ratio range of 6 to 24, the second gear has a gear ratio range of 3 to 6, the third gear has a gear ratio range of 2.67 to 8, and the fourth gear has a gear ratio range of 1.33 to 2.
Preferably, the first gear and the second gear have a step ratio range of 2 to 4, the second gear and the third gear have a step ratio range of 0.53 to 2.67, and the third gear and the fourth gear have a step ratio range of 2 to 4.
The beneficial effects of the invention are as follows: the invention establishes 4 forward speed ratios through different engagement modes of the brake or the clutch, and the three planetary rows of the invention can reach 2 or even higher in the proper k value (the ratio of the tooth number of the gear ring to the tooth number of the sun gear), so that the invention has the advantages of large-order ratio, compact structure, large bearing capacity and higher transmission efficiency, and is suitable for equipment such as high-power electric drive vehicles, large mining machinery, oilfield machinery and the like, and can be also applied to special vehicles.
Drawings
FIG. 1 is a schematic overall structure of embodiment 1 of the present invention;
fig. 2 is a schematic overall structure of embodiment 2 of the present invention.
Marked in the figure as: PG1: first row of planet, T1: first sun gear, J1: first planet carrier, Q1: first ring gear, PG2: second planet row, T2: second sun gear, J2: second planet carrier, Q2: second ring gear, PG3: third planet row, T3: third sun gear, J3: third planet carrier, Q3: third ring gear, Z1: first brake, Z2: second brake, Z3: third brake, C1: clutch, INPUT: input, OUTPUT: and outputting.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Example 1:
as shown in fig. 1, a large-order-ratio planetary transmission mechanism includes a first planetary row PG1, a second planetary row PG2, a third planetary row PG3, a first brake Z1, a second brake Z2, a third brake Z3, and a clutch C1;
the first planetary gear set PG1 is an inner-outer meshing double-planetary gear set, and comprises a first sun gear T1, a first gear ring Q1 and a first planet carrier J1;
the second planetary gear set PG2 is an inner-outer meshing single-planetary gear set and comprises a second sun gear T2, a second gear ring Q2 and a second planetary carrier J2;
the third planetary gear set PG3 is an inner and outer meshing double-planetary gear set and comprises a third sun gear T3, a third gear ring Q3 and a third planetary carrier J3;
a clutch C1 is connected between the third sun gear T3 and the third planet carrier J3;
the first planet carrier J1 is connected with the second sun gear T2; the first gear ring Q1 is connected with the second planet carrier J2 and the third sun gear T3.
The clutch C1 is a mechanical shifting element, a hydraulic shifting element or a pneumatic shifting element.
The first planet carrier J1 is an input end, and the third gear ring Q3 is an output end.
In this example, each planet row is in a proper k value range, and by setting three brakes and clutches to be engaged and disengaged in different manners, large-order-ratio four-gear transmission can be realized.
The first brake Z1, the second brake Z2 and the third brake Z3 are mechanical shifting elements, hydraulic shifting elements or pneumatic shifting elements, the first brake Z1 is used for braking the first sun gear T1, the second brake Z2 is used for braking the second gear ring Q2, and the third brake Z3 is used for braking the third planet carrier J3.
The present embodiment can realize a four-speed shift, specifically, a first speed is realized when the second brake Z2 and the third brake Z3 are engaged and the first brake Z1 and the clutch C1 are disengaged, a second speed is realized when the second brake Z2 and the clutch C1 are engaged and the first brake Z1 and the third brake Z3 are disengaged, a third speed is realized when the first brake Z1 and the third brake Z3 are engaged and the second brake Z2 and the clutch C1 are disengaged, and a fourth speed is realized when the first brake Z1 and the clutch C1 are engaged and the second brake Z2 and the third brake Z3 are disengaged.
The invention realizes the sequential change of the transmission ratio from first gear to fourth gear, and when the transmission ratio is switched from one gear to another gear, the gear shifting elements corresponding to the old gear are separated, and the gear shifting elements corresponding to the new gear are engaged.
The gear ratios and step ranges in this embodiment are verified in conjunction with table 1 as follows:
table 1 example 1 Shifting element State Table (open for disengaged, O for engaged)
The gear ratios determined according to the planetary mechanism principle in the present exemplary embodiment are listed in table 1, wherein K1, K2, K3 are the structural characteristic parameters of the first, second, and third planetary rows, respectively.
Specifically, K1 is the gear ratio of the first ring gear Q1 and the first sun gear T1, K2 is the gear ratio of the second ring gear Q2 and the second sun gear T2, and K3 is the gear ratio of the third ring gear Q3 and the third sun gear T3.
Because the actual ranges of the K values of the gear ratios of the gear ring and the sun gear cannot be too small or too large due to the fact that the shafts, the bearings, the teeth numbers, the overlap ratio and the like in the actual structure cannot be too small, the proper range of the K values of the inner and outer meshing single star rows can be 2-5, the proper range of the K values of the inner and outer meshing double star rows can be 2-4, namely, the range of the K1 and the K3 can be 2-4, and the range of the K2 can be 2-5.
The range of the transmission ratio which can be realized by each gear depends on the structural characteristic parameters of the planetary gear, specifically, according to the gear transmission ratio formula in the table 1 and the value ranges of K1, K2 and K3, the numerical values of K1, K2 and K3 are calculated by applying the formula in the table 1, the range of the transmission ratio of the first gear is 6-24, the range of the transmission ratio of the second gear is 3-6, the range of the transmission ratio of the third gear is 2.67-8, the range of the transmission ratio of the fourth gear is 1.33-2, the range of the step ratio of the first gear and the step ratio of the second gear is 2-4, the range of the step ratio of the second gear and the step ratio of the third gear is 0.53-2.67, and the range of the step ratio of the third gear and the step ratio of the fourth gear is 2-4.
For example, when k1=3.2, k2=4.5, k3=2, the first gear ratio is 11, the second gear ratio is 5.5, the third gear ratio is 2.9, and the fourth gear ratio is 1.45; 1. the step ratio of the second gear is 2, the step ratios of the second gear and the third gear are 1.9, and the step ratios of the third gear and the fourth gear are 2.
The above embodiment is a speed reducing mechanism, and if the input and output ends are exchanged, a speed increasing mechanism can be obtained, the range of the transmission ratio of the first gear can be 0.04-0.17, the range of the transmission ratio of the second gear can be 0.17-0.33, the range of the transmission ratio of the third gear can be 0.125-0.374, the range of the transmission ratio of the fourth gear can be 0.5-0.75, and the step ratio can be obtained according to similar analysis and is not described in detail herein.
In combination with the above related description, this embodiment includes three planetary rows, three brakes and one clutch, and by providing different engagement and disengagement modes of the three brakes and the clutch, a four-gear transmission ratio can be realized in a suitable k value range, and the step ratio can reach 2 or even more.
Example 2:
as shown in fig. 2, a large-step-ratio planetary transmission mechanism of this embodiment is similar to that of embodiment 1, and the main difference is that the third planetary gear set PG3 is disposed before the first planetary gear set PG1 and the second planetary gear set PG 2.
The first planet carrier J1 is connected with the second sun gear T2 and the third gear ring Q3; the first ring gear Q1 and the second carrier J2 are connected.
The third sun gear T3 is an input end, and the second planet carrier J2 is an output end.
Other than this, the other components, connection, transmission ratio, step ratio, etc. of this embodiment are the same as those of embodiment 1.
The foregoing is merely a preferred embodiment of the present invention, and it should be noted that modifications and improvements can be made by those skilled in the art without departing from the spirit of the present invention, and these should also be considered as the scope of the present invention, which does not affect the effect of the implementation of the present invention and the utility of the patent.
Claims (7)
1. The large-order-ratio planetary transmission mechanism is characterized by comprising a first planetary gear set PG1, a second planetary gear set PG2, a third planetary gear set PG3, a first brake Z1, a second brake Z2, a third brake Z3 and a clutch C1;
the first planetary gear set PG1 is an inner and outer meshing double planetary gear set, and comprises a first planetary carrier J1, a first sun gear T1 and a first gear ring Q1 which are respectively meshed with inner and outer planetary gears arranged on the first planetary carrier J1, wherein the first sun gear T1 is connected with a first brake Z1;
the second planetary gear set PG2 is an inner-outer meshing single-planetary gear set and comprises a second gear ring Q2, a second planetary carrier J2, a second gear ring Q2 meshed with planetary gears arranged on the second planetary carrier J2 and a second sun gear T2, and the second gear ring Q2 is connected with a second brake Z2;
the third planetary gear set PG3 is an inner and outer meshing double planetary gear set, and comprises a third planetary gear set J3, a third sun gear T3 and a third gear ring Q3 which are respectively meshed with inner and outer planetary gears arranged on the third planetary gear set J3, and the third planetary gear set J3 is connected with a third brake Z3;
a clutch C1 is connected between the third sun gear T3 and the third planet carrier J3;
the first planet carrier J1 is connected with the second sun gear T2, and the first gear ring Q1 is connected with the second planet carrier J2 and the third sun gear T3; or, the first planet carrier J1 is connected with the second sun gear T2, the third gear ring Q3 is connected, and the first gear ring Q1 is connected with the second planet carrier J2.
2. The large-ratio planetary transmission mechanism according to claim 1, wherein the clutch is a mechanical shift element, a hydraulic shift element, or a pneumatic shift element.
3. The large-order planetary transmission mechanism according to claim 1, wherein the first carrier is an input end, the third ring gear is an output end, or the third sun gear is an input end, and the second carrier is an output end.
4. The large-ratio planetary transmission mechanism according to claim 1, wherein the first brake, the second brake and the third brake are mechanical shift elements, hydraulic shift elements or pneumatic shift elements.
5. The high ratio planetary transmission mechanism according to claim 1, wherein first gear is achieved when the second brake and third brake are engaged and the first brake and clutch are disengaged, second gear is achieved when the second brake and clutch are engaged and the first brake and third brake are disengaged, third gear is achieved when the first brake and third brake are engaged and the second brake and third brake are disengaged, and fourth gear is achieved when the first brake and clutch are engaged and the second brake and third brake are disengaged.
6. The high ratio planetary transmission mechanism according to claim 5, wherein the first gear ratio range is 6 to 24, the second gear ratio range is 3 to 6, the third gear ratio range is 2.67 to 8, and the fourth gear ratio range is 1.33 to 2.
7. The large-ratio planetary transmission mechanism according to claim 5, wherein the first and second gear ranges from 2 to 4, the second and third gear ranges from 0.53 to 2.67, and the third and fourth gear ranges from 2 to 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110999885.0A CN113803425B (en) | 2021-08-27 | 2021-08-27 | Planetary speed change mechanism with large order ratio |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110999885.0A CN113803425B (en) | 2021-08-27 | 2021-08-27 | Planetary speed change mechanism with large order ratio |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113803425A CN113803425A (en) | 2021-12-17 |
| CN113803425B true CN113803425B (en) | 2023-12-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202110999885.0A Active CN113803425B (en) | 2021-08-27 | 2021-08-27 | Planetary speed change mechanism with large order ratio |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB738590A (en) * | 1952-09-09 | 1955-10-19 | Hobbs Transmission Ltd | Improvements in or relating to variable ratio power transmission apparatus |
| US3426618A (en) * | 1966-03-29 | 1969-02-11 | Ustav Pro Vyzkum Motorovych Vo | Hydromechanical multispeed drives |
| KR20050006742A (en) * | 2003-07-10 | 2005-01-17 | 현대자동차주식회사 | planetary gear set, clutches and brakes for a continuously variable transmission |
| WO2014072344A1 (en) * | 2012-11-06 | 2014-05-15 | Technische Universität München | Hub transmission for a bicycle |
| GB202015405D0 (en) * | 2019-10-08 | 2020-11-11 | Univ Jiangsu | No details |
-
2021
- 2021-08-27 CN CN202110999885.0A patent/CN113803425B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB738590A (en) * | 1952-09-09 | 1955-10-19 | Hobbs Transmission Ltd | Improvements in or relating to variable ratio power transmission apparatus |
| US3426618A (en) * | 1966-03-29 | 1969-02-11 | Ustav Pro Vyzkum Motorovych Vo | Hydromechanical multispeed drives |
| KR20050006742A (en) * | 2003-07-10 | 2005-01-17 | 현대자동차주식회사 | planetary gear set, clutches and brakes for a continuously variable transmission |
| WO2014072344A1 (en) * | 2012-11-06 | 2014-05-15 | Technische Universität München | Hub transmission for a bicycle |
| GB202015405D0 (en) * | 2019-10-08 | 2020-11-11 | Univ Jiangsu | No details |
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| Publication number | Publication date |
|---|---|
| CN113803425A (en) | 2021-12-17 |
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