CN107100965B - High ratio planetary gear shifting transmission - Google Patents
High ratio planetary gear shifting transmission Download PDFInfo
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- CN107100965B CN107100965B CN201710100269.0A CN201710100269A CN107100965B CN 107100965 B CN107100965 B CN 107100965B CN 201710100269 A CN201710100269 A CN 201710100269A CN 107100965 B CN107100965 B CN 107100965B
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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
- F16H3/62—Gearings having three or more central 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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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
- F16H3/62—Gearings having three or more central gears
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
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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
- F16H2003/447—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the set of orbital gears and the output
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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
- F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two 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
- F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
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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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
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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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to a planetary gear shifting transmission, comprising: a power input; a power output terminal; a front-stage transmission driven by a power input, the front-stage transmission having a fixed gear ratio, a front-stage sun gear, a front-stage planetary gear set, a front-stage planetary gear carrier, and a front-stage ring gear; a load-stage transmission driven by the forward-stage transmission and having a first load-stage sun gear, a second load-stage sun gear, a load-stage planetary gear, a first load-stage planetary carrier, and a first load-stage ring gear; and a double clutch device having: a first clutch for selectively coupling the first load stage sun gear to the forward stage planet carrier; and a second clutch for selectively coupling the second load stage sun gear to the front stage planetary carrier, wherein the double clutch device is arranged in an intermediate region which is located axially in space between the front stage transmission and the load stage transmission.
Description
Technical Field
The invention relates to a planetary transmission with a high overall transmission efficiency, in particular for use in motor vehicles equipped with a motor drive, wherein the planetary transmission comprises a plurality of gear stages each designed as a planetary transmission.
Disclosure of Invention
The invention is based on the following objectives: a planetary gear shifting transmission with a high overall transmission effect is achieved, which is characterized by a high mechanical efficiency.
According to the invention, the object is achieved by a planetary gear shifting transmission having:
-a power input;
-a power output;
a forward-stage transmission which is driven via a power input and has a fixed transmission ratio and which has a forward-stage sun gear, a forward-stage planetary gear set, a forward-stage planet carrier and a forward-stage ring gear, and a load-stage transmission which is driven via the forward-stage transmission and which has a first load-stage sun gear, a second load-stage sun gear, a load-stage planet gear, a first load-stage planet carrier and a first load-stage ring gear, and
a double clutch device having a first clutch for selectively coupling the first load stage sun gear to the front stage planet carrier, and a second clutch for selectively coupling the second load stage sun gear to the front stage planet carrier;
the double clutch device is arranged in an intermediate region which is located axially in space between the forward-stage transmission and the load-stage transmission.
In this way, it is advantageously possible to realize a planetary transmission in which the clutch mechanism designed as a double clutch is active in a transmission section in which an increase in the average torque and a corresponding decrease in the average rotational speed are already present.
The planetary transmission according to the invention can be advantageously configured such that the power input drives the front-stage sun gear and the power output is tapped from the load-stage transmission via the load-stage planetary gear carrier.
The planet gears of the first load stage planetary gear set preferably engage radially from the inside into the load stage ring gear. The planet gears preferably form a stepped planetary gear set together with the planet gears of the second load-stage planetary gear set. The planet gears of the first load stage planetary gear set, which then engage radially from the inside into the load stage ring gear, preferably have a pitch circle diameter which is smaller than the pitch circle diameter of the planet gears of the second load stage planetary gear set.
The planetary transmission according to the invention can be advantageously designed in such a way that it comprises a shaft journal which connects the first load stage sun gear to the inner rotor of the first clutch, wherein a hollow shaft is rotatably arranged on the shaft journal which connects the second load stage sun gear to the inner rotor of the second clutch. Between the hollow shaft and the bearing journal, a sliding bearing or preferably a rolling bearing can be provided, which enables a radial support of the two parts relative to one another.
The second load stage sun gear is closer to its associated second clutch than the first load stage gear is to its associated first clutch. By means of this particular nesting, an advantageous reduction in the load and radial transmission size of the load-stage planetary gear carrier is achieved, since the load-stage ring gear is radially immersed below the circumferential envelope circle of the planet gears of the second load-stage planetary gear set, which is concentric to the transmission axis, and thus has a smaller diameter than if said load-stage ring gear were paired with the planet gears of the second load-stage planetary gear set. The first load stage ring gear is also closer to the transmission output.
The two clutches of the dual clutch device are preferably designed as multi-plate clutches, the lamellae of which are guided in an alternating manner on the respective inner rotor and on the clutch housing in a rotationally fixed but axially displaceable manner. The clutch housings can in this case be directly rotationally rigidly coupled to the planet carrier of the upstream stage. The clutches of the dual clutch are preferably arranged axially next to one another and are preferably realized by using as many similar components as possible.
Furthermore, the planetary gear transmission according to the invention can advantageously be designed in such a way that a journal, which drives the first sun gear, and an input shaft, which drives the front stage sun gear, are centered relative to one another.
With the transmission according to the invention, two gears in the ranges i 15 and i 7.5 can be realized in a particularly advantageous manner, wherein the shaft of the simple upstream gear stage must be connected to the respective other shaft of the superimposed transmission stage on the output side. This is achieved according to the invention by means of a double clutch, the clutch housing of which is always connected to the web of the upstream stage, i.e. the planet carrier. The superimposed gear stages serving as load stages are preferably designed as a coupling transmission with stepped planetary gears. The double clutch is located axially between the forward stage and the superimposed gear stage providing the shifting function.
Drawings
Other details and features of the invention will appear from the following description taken in conjunction with the accompanying drawings. The figures show:
fig. 1 shows a schematic diagram for illustrating a configuration of a planetary transmission according to the invention according to a preferred embodiment of the invention, wherein a first load stage sun gear and a second load stage sun gear of a load stage can be selectively connected to a planet carrier of a preceding stage via a double clutch.
Detailed Description
The illustration according to fig. 1 shows an embodiment of the planetary transmission according to the invention. The planetary gear shift transmission includes: a power input terminal I1; a power output terminal O1; a front-mounted transmission VG, which is driven via a power input I1 and has a fixed gear ratio, having a front-mounted sun gear VS1, a front-mounted planetary gear set VP1, a front-mounted planetary gear carrier VC1 and a front-mounted ring gear VH1, which VH1 is fixed to the transmission housing G.
Furthermore, the planetary transmission according to the invention comprises a load-stage transmission LG which is driven by a forward-stage transmission VG and which has a first load-stage sun gear LS1, a second load-stage sun gear LS2, a first load-stage planetary gear set LP1, a second load-stage planetary gear set LP2, a first load-stage planetary carrier LC1 and a first load-stage ring gear LH 1.
The planetary transmission according to the invention is characterized in that it comprises a double clutch device DK having: a first clutch K1 for selectively coupling first load stage sun gear LS1 to the front stage planet carrier VC 1; and a second clutch K2 for selectively coupling the second load stage sun gear LS2 to the front stage planetary carrier LC1, wherein the double clutch device DK is arranged in an intermediate region which is located axially in space between the front stage transmission VG and the load stage transmission LG.
With the described configuration, it is possible to realize a planetary transmission in which the clutch mechanism DK designed as a double clutch acts in a transmission section in which an increase in the average torque and a corresponding decrease in the average rotational speed are already present.
By coupling the dual clutch device to the front-stage planetary gear carrier VC1, the power input I1, the front-stage sun gear VS1, the front-stage planetary gear carrier VC1 and the two load-stage sun gears LS1, LS2 and also the load-stage planetary gear carrier LC1 rotate in the same rotational direction, so that no reverse lubricant vortices form in the inner region. The planetary transmission according to the invention is therefore also characterized by high mechanical efficiency.
In the illustrated embodiment, power is extracted from the load stage transmission LG via the load stage planetary carrier LC 1. The planet gears of the first load stage planetary gear set LP1 are radially internally engaged in the load stage ring gear LH 1. The first and second load stage planetary gear sets LP1 and LP2 together form a stepped planetary gear set made up of stepped planet gears. The planet gears of the first load stage planetary gear set LP1 that engage in the load stage ring gear LH1 have a pitch circle diameter that is smaller than the pitch circle diameter of the planet gears of the second load stage planetary gear set LP 2. One planet gear of the first planetary gear set LP1 is rotationally rigidly connected to one planet gear of the second planetary gear set LP 2. The stepped planetary gear thus formed is rotatably mounted on planet pins anchored in a load-stage planetary carrier LC1 provided for achieving a power cut.
The planetary transmission according to the invention comprises a journal LW1, which connects the first load stage sun gear LS1 to the inner rotor BK1 of the first clutch K1. A hollow shaft LW2 is rotatably arranged on the journal LW1, which connects the second load stage sun gear LS2 to the inner rotor of the second clutch K2.
The two clutches K1, K2 are designed as multiplate clutches, wherein the dual clutch DK has a clutch housing DK1, which is rotationally rigidly coupled to the planet carrier VC1 of the front stage VS. The clutches K1, K2 of the dual clutch DK are arranged axially next to one another and are realized by using similar components.
The transmission described above can be designed such that the gear ratios in the respective shift states differ by a factor ranging from 1.4 to 2.4 and, in addition, a maximum gear ratio ranging from 11 to 17, in particular 15, can be achieved.
The first front sun gear LS1 can be driven by an electromechanical main drive motor in the following manner: the first forward stage sun gear VS1 is located directly on the rotor shaft of the engine. The engine and the described transmission according to the invention can be combined into a structural unit.
The operation of the double clutch DK is preferably performed by using an electromechanical actuator. The control of the actuator is preferably effected via an electronic control unit which also distributes the power of the drive engine during the shifting process in such a way that the most smooth possible shifting process is achieved.
Claims (10)
1. A planetary gear shifting transmission having:
-a power input (I1);
-a power output (O1);
-a front-stage transmission (VG) driven by the power input (I1), having a fixed gear ratio, having a front-stage sun gear (VS1), a front-stage planetary gear set (VP1), a front-stage planet gear carrier (VC1) and a front-stage ring gear (VH 1);
-a load-stage transmission (LG) driven by the forward-stage transmission (VG) having a first load-stage sun gear (LS1), a second load-stage sun gear (LS2), load-stage planet gears (LP1, LP2), a first load-stage planet gear carrier (LC1) and a first load-stage ring gear (LH1), and
-a double clutch Device (DK) having: a first clutch (K1) for selectively coupling the first load stage sun gear (LS1) to the forward stage planet carrier (VC 1); and a second clutch (K2) for selectively coupling the second load stage sun gear (LS2) to the forward stage planet carrier (VC 1);
-wherein the double clutch Device (DK) is arranged in an intermediate region, which is spatially axially between the front-stage transmission (VG) and the load-stage transmission (LG).
2. The planetary gear shifting transmission of claim 1,
it is characterized in that the preparation method is characterized in that,
power is extracted from the load stage transmission (LG) via the load stage planetary carrier (LC 1).
3. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the planet gears of the first load stage planetary gear set (LP1) are radially internally engaged in the load stage ring gear (LH 1).
4. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the first load stage planetary gear set (LP1) and the second load stage planetary gear set (LP2) together form a stepped planetary gear set having stepped planet gears.
5. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the planet gears of the first load stage planetary gear set (LP1) that engage in the load stage ring gear (LH1) have a pitch circle diameter that is smaller than the pitch circle diameter of the planet gears of the second load stage planetary gear set (LP 2).
6. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
a journal (LW1) is provided, which connects the first load stage sun gear (LS1) to the inner rotor (BK1) of the first clutch (K1), and a hollow shaft (LW2) is rotatably provided on the journal (LW1), which connects the second load stage sun gear (LS2) to the second clutch (K2).
7. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the two clutches (K1, K2) are designed as multi-plate clutches.
8. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the double clutch Device (DK) has a clutch housing which is rotationally rigidly coupled to a planet carrier (VC1) of the front-stage transmission (VG).
9. The planetary gear shifting transmission of claim 6,
it is characterized in that the preparation method is characterized in that,
the journal (LW1) and input shaft are centered relative to each other, the journal driving the first load stage sun gear (LS1), the input shaft driving the front stage sun gear (VS 1).
10. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the clutches (K1, K2) of the double clutch Device (DK) are arranged axially side by side and are realized at least in terms of clutch sheets by using the same type of components.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016202723.9 | 2016-02-23 | ||
| DE102016202723.9A DE102016202723B4 (en) | 2016-02-23 | 2016-02-23 | High-ratio epicyclic gearbox, in particular for an electrically operated motor vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107100965A CN107100965A (en) | 2017-08-29 |
| CN107100965B true CN107100965B (en) | 2022-06-03 |
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ID=59522361
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710100269.0A Active CN107100965B (en) | 2016-02-23 | 2017-02-23 | High ratio planetary gear shifting transmission |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107100965B (en) |
| DE (1) | DE102016202723B4 (en) |
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| DE102018130128A1 (en) | 2018-11-28 | 2020-05-28 | Schaeffler Technologies AG & Co. KG | Motor vehicle powertrain |
| DE102018130122A1 (en) | 2018-11-28 | 2020-05-28 | Schaeffler Technologies AG & Co. KG | Motor vehicle powertrain |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN107100965A (en) | 2017-08-29 |
| DE102016202723A1 (en) | 2017-08-24 |
| DE102016202723B4 (en) | 2018-01-11 |
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