CN107100966B - High ratio planetary gear shifting transmission - Google Patents
High ratio planetary gear shifting transmission Download PDFInfo
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- CN107100966B CN107100966B CN201710100281.1A CN201710100281A CN107100966B CN 107100966 B CN107100966 B CN 107100966B CN 201710100281 A CN201710100281 A CN 201710100281A CN 107100966 B CN107100966 B CN 107100966B
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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
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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
- F16H3/44—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
- 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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- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
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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
- F16H2200/2007—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
- F16H2200/2002—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
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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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
Abstract
The invention relates to a planetary gear shifting transmission, comprising: a power input; a power output terminal; a planetary gear sub-transmission which is driven via a power input and whose transmission effect can be changed in a switchable manner via a fixed transmission element, having a first sun gear, a first planetary gear set, a first planet carrier and a first ring gear; a load stage having a fixed gear ratio, the load stage being driven by the output of the planetary sub-transmission and forming a power output, the load stage having a load stage sun gear, a load stage planetary gear set, a load stage planet gear carrier and a load stage ring gear; a brake device having a first brake for selectively fixing a first rotational part of the planetary gear set and a second brake for selectively fixing a second rotational part of the planetary gear set, wherein the brake device is arranged on a side of the planetary gear set facing away from the load stage.
Description
Technical Field
The invention relates to a planetary transmission with a high overall transmission efficiency, in particular for use in a motor vehicle with an electromechanical drive, wherein the planetary transmission comprises a plurality of transmission stages each designed as a planetary transmission.
Disclosure of Invention
The present invention is based on the object of creating a planetary transmission with a high overall transmission which is characterized by a compact design, favorable shifting behavior and high mechanical efficiency.
The object is achieved according to the invention by a planetary transmission having:
-a power input;
-a power output;
a planetary gear sub-transmission which is driven via a power input and whose transmission effect can be changed in a switchable manner via a fixed transmission component, having a first sun gear, a first planetary gearset, a first planet carrier and a first ring gear;
-a load stage with a fixed gear ratio, which is driven by the output of the planetary sub-transmission and forms a power output, which load stage has a load stage sun gear, a load stage planetary gear set, a load stage planet gear carrier and a load stage ring gear, and
-a brake device having a first brake for selectively fixing a first rotational part of the planetary gear transmission and a second brake for selectively fixing a second rotational part of the planetary gear transmission;
wherein the braking device is arranged on a side of the planetary gear set facing away from the load stage.
In this way, it is advantageously possible to implement a planetary transmission in which the shifting function can be implemented in a transmission region with a low torque load and the torque increase to the output torque can be implemented by a load stage arranged directly adjacent to the shiftable transmission region. Furthermore, the brake device can be realized as a compact component which is accessible from the side of the transmission input in a maintenance-friendly manner and which can be mounted on the transmission housing.
With the transmission according to the invention, two gears in the range of i 15 and i 7.5 can be realized in a particularly advantageous manner, wherein for setting the required transmission ratio, one shaft must be braked in each case relative to the housing for each gear. For this purpose, the brake device can be designed in the form of a dual clutch, the clutch housing of which is permanently fixed by: the clutch housing is connected to the housing, for example. The transmission according to the invention can be shifted in a particularly advantageous manner asynchronously under load conditions.
According to a particularly preferred embodiment of the invention, the planetary transmission is designed such that the load stage sun gear is the power input of the load stage. The load stage sun gear is arranged here concentrically to the main axis of the transmission and engages radially from the inside into the planet gears of the load stage planetary gear set.
The planetary transmission can be designed such that the first ring gear, the first planet carrier and/or the first or second ring gear can be fixed in a switchable manner. Furthermore, it is possible for the planetary gear sub-transmission to be designed such that it comprises a second sun gear, and for the second sun gear to be fixed in a switchable manner via a brake device.
The driving of the load stage can advantageously be realized by: the load stage sun gear is rotationally rigidly coupled to the first planetary gear carrier and is driven by the first planetary gear carrier. Alternatively, it is also possible for the load cascade to be connected to the superimposed sub-transmission in the following manner: the load stage sun gear is rotationally rigidly coupled to and driven by the first ring gear.
By means of the concept according to the invention, a high-ratio two-speed transmission is achieved in an advantageous manner. For shifting, a double clutch, in particular a double brake, is used. With the transmission described below, two gears in the range of i 15 and i 7.5 can be implemented, wherein one shaft is braked in each gear relative to the housing. For this purpose, a dual clutch is used, the clutch housing of which is fixedly connected to the transmission housing. The superimposed partial transmissions that implement the shifting function are designed as coupled transmissions. Common to all variants is the load stage on the output side. The gear stages can be spatially separated from the double clutch.
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 the configuration of a planetary transmission according to the invention according to a first preferred embodiment of the invention, wherein a first ring gear and a second sun gear of the planetary transmission can be selectively fixed by means of a brake device;
fig. 2 shows a schematic diagram for illustrating the configuration of a planetary transmission according to the invention according to a second preferred embodiment of the invention, wherein the first ring gear and the second sun gear of the planetary transmission can likewise be selectively fixed;
fig. 3 shows a schematic diagram for illustrating a configuration of a planetary gear transmission according to the present invention in which a first planetary gear carrier and a second sun gear of the planetary gear transmission may be selectively fixed, according to a third preferred embodiment of the present invention;
fig. 4 shows a schematic diagram for illustrating a configuration of a planetary gear transmission according to the present invention according to a fourth preferred embodiment of the present invention, in which a first ring gear and a second ring gear of the planetary gear transmission may be selectively fixed.
Detailed Description
The illustration according to fig. 1 shows an example of a planetary gear set transmission according to the invention in a first embodiment. The planetary gear shift transmission includes: a power input terminal I1; a planetary gear sub-transmission G1, which is driven via a power input I1 and whose transmission effect can be changed in a switchable manner via a fixed transmission element, has a first sun gear S1, a first planetary gear set P1, a first planet carrier C1 and a first ring gear H1. The planet gears of the first planetary gear set P1 are mounted on the first planet carrier C1 and are radially inwardly engaged in the first ring gear H1.
The planetary transmission according to the invention furthermore comprises a load stage LS with a fixed transmission ratio, which is driven via the output G1A of the planetary sub-transmission G1 and forms the power output O1 of the planetary transmission. Load stage LS includes load stage sun gear LS1, load stage planetary gear set LP1, load stage planet carrier LC1, and load stage ring gear LH 1. The load-stage sun gear LS1 is driven via the output G1A of the planetary sub-transmission G1 and engages radially from the inside into the planetary gearset LP1 from the transmission axis. The planet gears of planetary gearset LP1 are mounted on the planet carrier LC1 of the load stage and are radially engaged from the inside into the ring gear LH1 of the load stage LS. The ring gear LH1 is fixed in the transmission case G. The planet carrier LC1 of the load stage LS drives its power output O1.
In the planetary transmission according to the invention, the shifting function is implemented by: a brake device BR is provided, which comprises: a first brake BR1 for selectively fixing a first rotary member of the planetary sub-transmission G1; and a second brake BR2 for selectively fixing a second rotating member of the planetary sub-transmission G1. The brake BR is arranged on the side of the planetary gear unit G1 facing away from the non-shiftable load stage LS. It is thereby possible to implement the shifting function in a transmission range with a low torque load and to increase the torque to the output torque by means of a load stage LS, which can be arranged directly adjacent to the shiftable transmission range G1 due to the provision of the brake BR. Furthermore, the brake BR can be realized as a compact assembly which is accessible from the side of the transmission input in a manner which is advantageous in terms of maintenance. With the illustrated transmission configuration, two gears in the range of i 15 and i 7.5 can be realized in a particularly advantageous manner, wherein one shaft must be braked in each case relative to the housing G for each gear. In this regard, the brake BR can be designed as a dual clutch, the clutch housing BRC of which is permanently fixed by: the clutch housing is connected to the housing G, for example.
The first sun gear S1 is the power input of the planetary sub-transmission G1, and the load stage sun gear LS1 is the power input of the load stage LS. The two sub-transmissions can be kinematically coupled by: the load stage sun gear LS1 is rotationally rigidly coupled to the first planetary gear carrier C1 and is in turn driven by the first planetary gear carrier.
In the exemplary embodiment shown here, planetary sub-transmission G1 includes, in addition to first planet carrier C1, a further second planet carrier C2, a second sun gear S2, second planet gears P2 and a second ring gear H2. The second sun gear S2 is engaged into the second planetary gear P2 from the inside in the radial direction. The second planet gears P2 are supported on the second planet carrier C2 and are radially inwardly engaged in the second ring gear H2. The second planet carrier C2 is switchably fixable via a first brake BR1 of the brake device BR. The second sun gear S2 of the planetary sub-transmission G1 may be selectively fixed via a second brake BR2 of the brake device BR. The second planet carrier C2 is rotationally rigidly coupled to the first ring gear H1. Thereby, the first ring gear H1 may also be fixed via the first brake BR 1. The second ring gear H2 is rotationally rigidly coupled to the first planetary gear carrier C1.
The standard transmission ratio of the gear pairs of the first sun gear S1, the first planetary gear set P1 and the first ring gear H1 is-2 as here. The standard gear ratio of the gear pair of the second sun gear S2, the second planetary gear set P2 and the second ring gear H2 is here for example-3. The standard gear ratio of the gear pairs of the first load stage sun gear LS1, the first load stage planetary gear set LP1 and the load stage ring gear LH1 is here for example-4.
The illustration according to fig. 2 shows a second exemplary embodiment of the planetary transmission according to the invention. The planetary gear shifting transmission includes a power input I1; a planetary gear sub-transmission G1 which is driven via a power input I1 and whose transmission effect can in turn be changed in a switchable manner via a fixed transmission element, has a first sun gear S1, a first planetary gear set P1, a first planet carrier C1 and a first ring gear H1.
The planetary transmission according to the invention furthermore comprises a load stage LS with a fixed transmission ratio, which is driven via the output G1A of the planetary sub-transmission G1 and forms the power output O1 of the planetary transmission. The load stage LS includes a load stage sun gear LS1, a load stage planetary gear set LP1, a load stage planet carrier LC1, and a load stage ring gear LH 1. The load-stage sun gear LS1 is driven via the output G1A of the planetary sub-transmission G1 and engages radially from the inside into the planetary gearset LP1 from the transmission axis. The planet gears of planetary gearset LP1 are mounted on the planet carrier LC1 of the load stage and are radially engaged from the inside into the ring gear LH1 of the load stage LS. The ring gear LH1 is fixed in the transmission case G. The planet carrier LC1 of the load stage LS drives its power output O1.
In the second embodiment of the planetary transmission according to the invention, the shifting function is again realized by: a brake device BR is provided, which comprises: a first brake BR1 for selectively fixing a first rotating member of the planetary gear transmission; and a second brake BR2 for selectively fixing a second rotating member of the planetary gear transmission. The brake BR is arranged here, as in the variant according to fig. 1, on the side of the planetary transmission facing away from the non-shiftable load stage LS. It is thus also possible to implement the shifting function in a transmission range with a low torque load and to increase the torque to the output torque by means of a load stage LS, which can be arranged directly adjacent to the shiftable transmission range G1 due to the provision of the brake BR. Furthermore, the brake BR can be realized as a compact assembly which is accessible from the side of the transmission input in a manner which is advantageous in terms of maintenance. With the illustrated transmission configuration, two gears in the range of i 15 and i 7.5 can be realized in a particularly advantageous manner, wherein one shaft must be braked in each case relative to the housing G for each gear. In this regard, the brake BR can be designed as a dual clutch, the clutch housing BRC of which is permanently fixed by: the clutch housing is connected to the housing G, for example.
The first sun gear S1 is the power input of the planetary sub-transmission G1, and the load stage sun gear LS1 is the power input of the load stage LS. The two sub-transmissions are kinematically coupled by: the load stage sun gear LS1 is rotationally rigidly coupled to and in turn driven by the first planetary gear carrier C1.
In the exemplary embodiment shown here, the first planetary gear carrier C1 also supports the planet gears of the second planetary gear set P2, which are in engagement with the planet gears of the first planetary gear set P1, in addition to the planet gears of the first planetary gear set P1. Furthermore, the planetary sub-transmission G1 comprises a second sun gear S2, which engages radially from the inside into the planet gears of the second planetary gear set P2. The planet gears of the second planetary gear set P2 are supported on the first planet gear carrier C1. The first ring gear H1 is switchably fixed via a first brake BR1 of the brake device BR. The second sun gear S2 of the planetary sub-transmission G1 is selectively fixable via a second brake BR2 of the brake device BR.
The illustration according to fig. 3 shows a third exemplary embodiment of the planetary transmission according to the invention. The planetary gear shifting transmission includes a power input I1; a planetary gear sub-transmission G1, which is driven via a power input I1 and whose gearing effect can be changed in a switchable manner via a fixed transmission element, has a first sun gear S1, a first planetary gear set P1, a first planet carrier C1 and a first ring gear H1.
The planetary transmission according to the invention furthermore comprises a load stage LS with a fixed transmission ratio, which is driven via the output G1A of the planetary sub-transmission G1 and forms the power output O1 of the planetary transmission. The load stage LS includes a load stage sun gear LS1, a load stage planetary gear set LP1, a load stage planet carrier LC1, and a load stage ring gear LH 1. The load-stage sun gear LS1 is driven via the output G1A of the planetary sub-transmission G1 and engages radially from the inside into the planetary gearset LP1 from the transmission axis. The planet gears of planetary gearset LP1 are mounted on the planet carrier LC1 of the load stage and are radially engaged from the inside into the ring gear LH1 of load stage 1. The ring gear LH1 is fixed in the transmission case G. The planet carrier LC1 of the load stage LS drives its power output O1.
In the planetary transmission according to the present invention, the shift function is realized by: a brake device BR is provided, which comprises: a first brake BR1 for selectively fixing a first rotating member of the planetary gear transmission; and a second brake BR2 for selectively fixing a second rotating member of the planetary gear transmission. The brake device BR is arranged on the side of the planetary gear set facing away from the non-shiftable load stage LS. In this way, it is possible to implement the shifting function in a transmission range with a low torque load and to increase the torque to the output torque by means of a load stage LS, which can be arranged directly adjacent to the shiftable transmission range G1 due to the provision of the brake BR. Furthermore, the brake BR can be realized as a compact assembly which is accessible from the side of the transmission input in a manner which is advantageous in terms of maintenance. With the illustrated transmission configuration, two gears in the range of i 15 and i 7.5 can be realized in a particularly advantageous manner, wherein one shaft must be braked in each case relative to the housing G for each gear. In this regard, the brake BR can be designed as a dual clutch, the clutch housing BRC of which is permanently fixed by: the clutch housing is connected to the housing G, for example.
The first sun gear S1 is the power input of the planetary sub-transmission G1, and the load stage sun gear LS1 is the power input of the load stage LS. The two sub-transmissions are kinematically coupled by: the load stage sun gear LS1 is rotationally rigidly coupled to the first ring gear H1 and is in turn driven by the first ring gear H1.
In the exemplary embodiment shown here, the first planetary gear carrier C1 also supports the planet gears of the second planetary gear set P2, which are in engagement with the planet gears of the first planetary gear set P1, in addition to the planet gears of the first planetary gear set P1. Furthermore, the planetary sub-transmission G1 comprises a second sun gear S2, which engages radially from the inside into the planet gears of the second planetary gear set P2. The planet gears of the second planetary gear set P2 are supported on the first planet gear carrier C1. The first planet carrier C1 is switchably fixed via a first brake BR1 of the brake device BR. The second sun gear S2 of the planetary sub-transmission G1 is selectively fixable via a second brake BR2 of the brake device BR.
The illustration according to fig. 4 shows a fourth exemplary embodiment of the planetary transmission according to the invention. The planetary gear shifting transmission includes a power input I1; a planetary gear sub-transmission G1 which is driven via a power input I1 and whose gearing effect can be changed in a switchable manner by means of fixed transmission elements and which has a first sun gear S1, a first planetary gear set P1, a first planet carrier C1 and a first ring gear H1 and a second ring gear H2 and a second planetary gear set P2.
The planetary transmission according to the invention furthermore comprises a load stage LS with a fixed transmission ratio, which is driven via the output G1A of the planetary sub-transmission G1 and forms the power output O1 of the planetary transmission. The load stage LS includes a load stage sun gear LS1, a load stage planetary gear set LP1, a load stage planet carrier LC1, and a load stage ring gear LH 1. The load-stage sun gear LS1 is driven via the output G1A of the planetary sub-transmission G1 and engages radially from the inside into the planetary gearset LP1 from the transmission axis. The planet gears of planetary gearset LP1 are mounted on the planet carrier LC1 of the load stage and are radially engaged from the inside into the ring gear LH1 of load stage 1. The ring gear LH1 is fixed in the transmission case G. The planet carrier LC1 of the load stage LS drives its power output O1.
In the planetary transmission according to the present invention, the shift function is realized by: a brake device BR is provided, which comprises: a first brake BR1 for selectively fixing a first rotating member of the planetary gear transmission; and a second brake BR2 for selectively fixing a second rotating member of the planetary gear transmission. In this case, as in all the embodiments described above, the brake BR is arranged on the side of the planetary gear unit G1 facing away from the non-shiftable load stage LS. In this way, it is possible to implement the shifting function in a transmission range with a low torque load and to increase the torque to the output torque by means of a load stage LS, which can be arranged directly adjacent to the shiftable transmission range G1 due to the provision of the brake BR. Furthermore, the brake BR can be realized as a compact assembly which is accessible from the side of the transmission input in a manner which is advantageous in terms of maintenance. With the illustrated transmission configuration, two gears in the range of i 15 and i 7.5 can be realized in a particularly advantageous manner, wherein one shaft must be braked in each case relative to the housing G for each gear. In this regard, the brake BR can be designed as a dual clutch, the clutch housing BRC of which is permanently fixed by: the clutch housing is connected to the housing G, for example.
The first sun gear S1 is the power input of the planetary sub-transmission G1, and the load stage sun gear LS1 is the power input of the load stage LS. The two sub-transmissions are kinematically coupled by: the load stage sun gear LS1 is rotationally rigidly coupled to the first planetary gear carrier C1 and is in turn driven by the first planetary gear carrier.
In the exemplary embodiment shown here, the first planetary gear carrier C1 also carries the planet gears of the second planetary gear set P2 in addition to the planet gears of the first planetary gear set P1, which are arranged coaxially with the planet gears of the first planetary gear set P1 and are coupled in a rotationally rigid manner therewith in order to form what are known as stepped planet gears. Furthermore, the planetary sub-transmission G1 comprises a second ring gear H2, into which the planet gears of the second planetary gear set P2 engage from the inside in the radial direction. The planet gears of the second planetary gear set P2 are supported on the first planet gear carrier C1. The first ring gear H1 is switchably fixed via a first brake BR1 of the brake device BR. The second ring gear H2 of the planetary sub-transmission G1 is selectively fixable via a second brake BR2 of the brake device BR.
The transmission described above can be designed such that the gear ratio differences in the respective shift states range from a factor of 1.4 to 2.4 and, in addition, a maximum gear ratio in the range from 11 to 17, in particular a maximum gear ratio of 15, can be achieved.
The drive of the first sun gear S1 can be realized by the electromechanical main drive motor by: the first sun gear S1 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 brake BR is preferably actuated by means of an electromechanical actuator. The control of the actuator is preferably effected via an electronic control unit, which also distributes the power for driving the engine during the shifting operation, so that a shifting operation which is as free of shocks as possible is achieved.
Claims (10)
1. A planetary gear shifting transmission having:
-a power input (I1);
-a power output (O1);
-a planetary gear sub-transmission (G1) which is driven via the power input (I1) and whose gearing effect can be changed in a switchable manner by means of a fixed transmission element, having a first sun gear (S1), a first planetary gear set (P1), a first planetary gear carrier (C1) and a first ring gear (H1);
-a Load Stage (LS) with a fixed gear ratio, which is driven by an output (G1A) of the planetary sub-transmission (G1) and forms the power output (O1) of the planetary transmission, which has a load stage sun gear (LS1), a load stage planetary gear set (LP1), a load stage planet gear carrier (LC1) and a load stage ring gear (LH1), and
-a braking device (BR) having: a first brake (BR1) for selectively fixing a first rotational member of the planetary gear transmission (G1); and a second brake (BR2) for selectively fixing a second rotating member of the planetary gear transmission (G1),
-wherein the braking device (BR) is arranged on a side of the planetary sub-transmission (G1) facing away from the Load Stage (LS).
2. The planetary gear shifting transmission of claim 1,
it is characterized in that the preparation method is characterized in that,
the brake device (BR) is of the dual clutch type, the clutch housing (BRC) of which is permanently fixed.
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 first sun gear (S1) is the power input of the planetary gear transmission (G1).
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 ring gear (H1) can be fixed in a switchable manner.
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 first planet gear carrier (C1) can be fixed in a switchable manner.
6. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the planetary sub-transmission (G1) comprises a second sun gear (S2), and the second sun gear (S2) is switchably fixed via the brake device (BR).
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 planetary sub-transmission comprises a second ring gear (H2), and the second ring gear (H2) is switchably fixable.
8. The planetary gear shifting transmission of claim 7,
it is characterized in that the preparation method is characterized in that,
the second ring gear (H2) is rotationally rigidly coupled to the first planetary gear carrier (C1).
9. The planetary gear shift transmission according to claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the load stage sun gear (LS1) is the power input of the Load Stage (LS).
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 load stage sun gear (LS1) is rotationally rigidly coupled to the first planetary gear carrier (C1) and is driven by the first planetary gear carrier, or the load stage sun gear (LS1) is rotationally rigidly coupled to the first ring gear (H1) and is driven by the first ring gear.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016202727.1A DE102016202727A1 (en) | 2016-02-23 | 2016-02-23 | High-ratio epicyclic gearbox, in particular for an electrically operated motor vehicle |
| DE102016202727.1 | 2016-02-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107100966A CN107100966A (en) | 2017-08-29 |
| CN107100966B true CN107100966B (en) | 2021-12-24 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710100281.1A Active CN107100966B (en) | 2016-02-23 | 2017-02-23 | High ratio planetary gear shifting transmission |
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| Country | Link |
|---|---|
| CN (1) | CN107100966B (en) |
| DE (1) | DE102016202727A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017010868A1 (en) * | 2017-11-24 | 2019-05-29 | Daimler Ag | Transmission device for an electric drive system, in particular of a motor vehicle, and electric drive system for a motor vehicle |
| CN108725583B (en) * | 2018-05-29 | 2021-04-02 | 山推工程机械股份有限公司 | Variable speed steering device, bulldozer and engineering machinery |
| DE102019119946B3 (en) * | 2019-07-24 | 2020-12-24 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle with a non-rotatable ring gear-planet carrier double bond |
| DE102019217155A1 (en) * | 2019-11-07 | 2021-05-12 | Zf Friedrichshafen Ag | Electric drive for a vehicle |
| DE102020105492A1 (en) | 2020-03-02 | 2021-09-02 | Schaeffler Technologies AG & Co. KG | Power shiftable transmission device for an electric drive of a vehicle |
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| Publication number | Publication date |
|---|---|
| CN107100966A (en) | 2017-08-29 |
| DE102016202727A1 (en) | 2017-08-24 |
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