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CN107100965A - High ratio planetary gear shifting transmission - Google Patents

High ratio planetary gear shifting transmission Download PDF

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Publication number
CN107100965A
CN107100965A CN201710100269.0A CN201710100269A CN107100965A CN 107100965 A CN107100965 A CN 107100965A CN 201710100269 A CN201710100269 A CN 201710100269A CN 107100965 A CN107100965 A CN 107100965A
Authority
CN
China
Prior art keywords
load stage
prestage
planetary
gear
planetary gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201710100269.0A
Other languages
Chinese (zh)
Other versions
CN107100965B (en
Inventor
托尔斯滕·比尔曼
弗朗茨·屈特
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN107100965A publication Critical patent/CN107100965A/en
Application granted granted Critical
Publication of CN107100965B publication Critical patent/CN107100965B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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 dual 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

The planetary gear manual transmission of high transmission ratio
Technical field
It is motor-driven particularly for being used in the present invention relates to a kind of planetary gear manual transmission that there is height to be always driven effect Che Zhong, the motor vehicle is equipped with motor driver, wherein the planetary gear manual transmission includes multiple be respectively structured as The speed change level of planetary transmission.
The content of the invention
The present invention is based on following purposes：A kind of planetary gear manual transmission that there is height to be always driven effect is realized, it is described Planetary gear manual transmission is characterised by high mechanical efficiency.
According to the present invention, the purpose is realized by a kind of planetary gear manual transmission, the planetary gear gearshift Speed changer has：
- power input；
- power take-off；
- prestage speed changer, the prestage speed changer is driven by power input, and the prestage speed changer has Fixed gearratio, the prestage speed changer has prestage sun gear, prestage planetary gearsets, prestage planetary gear Frame and prestage gear ring, and
- load stage speed changer, the load stage speed changer is driven by prestage speed changer, the load stage speed change utensil There are the first load stage sun gear, the second load stage sun gear, load stage planetary gear, the first load stage pinion frame and first Load stage gear ring, and
- double clutch device, the double clutch device, which has, to be used to optionally couple the first load stage sun gear First clutch onto prestage pinion frame, and for the second load stage sun gear optionally to be coupled into prestage Second clutch on pinion frame；
- wherein double clutch device is set in the middle region, and the intermediate region is spatially axially located at preposition Between level speed changer and load stage speed changer.
Thus, in an advantageous manner it is possible that realize following planetary gear manual transmissions, changed in the planetary gear In shift transmission, it is configured to the clutch mechanism of double clutch and is worked in following speed changer section, in the speed changer portion There is average torque rise in section and correspondingly mean speed is reduced.
It can be configured in an advantageous manner according to the planetary gear manual transmission of the present invention so that power input drives Dynamic prestage sun gear, and power interception is carried out from load stage speed changer via load stage pinion frame.
The planetary gear of first load stage planetary gearsets is preferably radially from interior bonds into load stage gear ring.The row Planetary gear of the star gear preferably with the second load stage planetary gearsets is collectively forming classification planetary gearsets.First load stage row Star gear train this then radially from interior bonds to the planetary gear in load stage gear ring herein preferably have following pitch circle Diameter, the pitch diameter is less than the planetary pitch diameter of the second load stage planetary gearsets.
It can be configured in an advantageous manner according to the planetary gear manual transmission of the present invention so that the planetary gear Manual transmission includes axle journal, and the axle journal connects the internal rotor of the first load stage sun gear and first clutch, wherein Rotatably arranged with there is hollow shaft on the axle journal, the hollow shaft will turn in the second load stage sun gear and second clutch Son connection.Between the hollow shaft and axle journal, sliding bearing or preferred rolling bearing, the sliding bearing or rolling can be provided with Dynamic bearing can realize the mutual radial support of two parts.
With the first load step cone adjacent to compared with first clutch associated with it, the second load stage sun gear adjacent to Its associate second clutch closer to.By the special nesting, favourable load and the footpath of load stage pinion frame are obtained To the reduction of transmission dimensions, because load stage gear ring is radially submerged to the planetary of the second load stage planetary gearsets With variator axis it is concentric circular envelope circle under, and and then with the load stage gear ring and the second load stage planetary gearsets Planetary gear it is paired when compare have less diameter.First load stage gear ring is also closer to transmission output.
Two clutches of double clutch device are preferably configured as multidisc clutch, and its thin slice is in an alternating manner corresponding Internal rotor on and be directed torsionally but axially displaceably on clutch housing.Those clutch housings herein can be straight Switch through dynamic be rigidly coupled on the pinion frame of prestage.The clutch of double clutch preferably axially abreast set and It is preferred that being realized by using similar component as much as possible.
In addition, can be configured in an advantageous manner according to the planetary gear manual transmission of the present invention so that axle journal phase To feeling relieved each other, to drive the first sun gear and input shaft, the input shaft drives prestage sun gear.
By the speed changer according to the present invention, the scope in i=15 and i=7.5 can be realized in a particularly advantageous manner In two gears, wherein the axle of simple prestage must be connected with each other axle of the superposition speed change level of outlet side.This Realized according to the present invention by means of double clutch, disc, the i.e. planet of the bell housing of the double clutch all the time with prestage Tooth rest is connected.The superposition speed change level for being used as load stage is preferably configured as the planetary coupling speed changer with classification. Double clutch is axially located between prestage and the superposition speed change level for providing gearshift function.
Brief description of the drawings
The other details and feature of the present invention are drawn from description below in conjunction with the accompanying drawings.Accompanying drawing is shown：
Fig. 1 is shown for illustrating a planet tooth according to the present invention preferred embodiment according to the present invention The schematic diagram of the construction of manual transmission is taken turns, wherein the first load stage sun gear and the second load stage sun gear of load stage can be with Optionally it is connected via double clutch with the pinion frame of prestage.
Embodiment
One embodiment of planetary gear manual transmission according to the present invention is shown according to Fig. 1 view.The planet Gear manual transmission includes：Power input I1；Power take-off O1；Prestage speed changer VG, the prestage speed changer Driven by power input I1, the prestage speed changer has fixed gearratio, before the prestage speed changer has A grade sun gear VS1, prestage planetary gearsets VP1, prestage pinion frame VC1 and prestage gear ring VH1 are put, it is described preposition Level gear ring VH1 is fixed on case of transmission G.
In addition, including load stage speed changer LG, the load stage speed change according to the planetary gear manual transmission of the present invention Device is driven by prestage speed changer VG, and the load stage speed changer has the first load stage sun gear LS1, the second load stage too Sun wheel LS2, the first load stage planetary gearsets LP1, the second load stage planetary gearsets LP2, the first load stage pinion frame LC1 and the first load stage gear ring LH1.
It is characterised by according to the planetary gear manual transmission of the present invention, the planetary gear manual transmission includes double Clutch apparatus DK, the double clutch device has：First clutch K1, for optionally by the first load stage sun gear LS1 is coupled on prestage pinion frame VC1；With second clutch K2, for optionally by the second load stage sun gear LS2 is coupled on prestage pinion frame LC1, and wherein double clutch device DK is set in the middle region, the middle area Domain is spatially axially located between prestage speed changer VG and load stage speed changer LG.
Pass through described construction, it is possible to realize following planetary gear manual transmissions, changed in the planetary gear In shift transmission, it is configured to the clutch mechanism DK of double clutch and is worked in following speed changer section, in the speed changer There is average torque rise in section and correspondingly mean speed is reduced.
It is connected on prestage pinion frame VC1 and is realized by double clutch device, power input I1, prestage is too Sun wheel VS1, prestage pinion frame VC1 and two load stage sun gear LS1, LS2 and also load stage pinion frame LC1 is rotated with identical rotation direction so that do not form reverse lubricant vortex in region internally.According to the present invention's Therefore the feature of planetary gear manual transmission lies also in high mechanical efficiency.
In the illustrated embodiment, power is carried out from load stage speed changer LG via load stage pinion frame LC1 to cut Take.First load stage planetary gearsets LP1 planetary gear is radially from interior bonds into load stage gear ring LH1.First load Level planetary gearsets LP1 and the second load stage planetary gearsets LP2 is collectively forming the classification planet being made up of classification planetary gear Gear train.The first load stage planetary gearsets LP1 planetary gear being joined in load stage gear ring LH1 has following section herein Circular diameter, the pitch diameter is less than the second load stage planetary gearsets LP2 planetary pitch diameter.First planet tooth One planetary gear rotation of wheel group LP1 each planetary gear and the second planetary gearsets LP2 is rigidly attached.Such shape Into classification planetary gear rotatably supported on planet pin, the planet pin, which is anchored at, to be set to for realizing power interception In load stage pinion frame LC1.
Axle journal LW1 is included according to the planetary gear manual transmission of the present invention, the axle journal is by the first load stage sun gear LS1 is connected with first clutch K1 internal rotor BK1.Rotatably arranged with hollow shaft LW2 on the axle journal LW1, the sky Second load stage sun gear LS2 is connected by heart axle with second clutch K2 internal rotor.
The two clutches K1, K2 are configured to multidisc clutch, and wherein double clutch DK has clutch housing DK1, It is connected on prestage VS pinion frame VC1 to the clutch housing rotational stiffness.Double clutch DK clutch K1, K2 is axially abreast set and realized by using similar component.
The speed changer that is described above it can be designed so that gearratio differed in corresponding gearshift condition scope from 1.4 to 2.4 factor, and be furthermore possible to realize scope from 11 to 17, in particular 15 maximum transmission ratio.
First prestage sun gear LS1 driving can be accomplished in the following manner by electromechanical main driving engine： First prestage sun gear VS1 is on the armature spindle of the engine.Engine and it is described according to the present invention Speed changer can be combined into construction unit.
Double clutch DK operation is preferably carried out by using electromechanical actuator.The control of the actuator is preferred Carried out via electronic-controlled installation, the electronic-controlled installation will also drive the power distribution of engine during shift process Into so that realize shift process as stable as possible.

Claims (10)

1. a kind of planetary gear manual transmission, has：
- power input (I1)；
- power take-off (O1)；
- prestage speed changer (VG), the prestage speed changer is driven by the power input (I1), and the prestage becomes Fast utensil has fixed gearratio, and the prestage speed changer has prestage sun gear (VS1), prestage planetary gearsets (VP1), prestage pinion frame (VC1) and prestage gear ring (VH1)；
- load stage speed changer (LG), the load stage speed changer is driven by the prestage speed changer (VG), the load stage Speed changer have the first load stage sun gear (LS1), the second load stage sun gear (LS2), load stage planetary gear (LP1, LP2), the first load stage pinion frame (LC1) and the first load stage gear ring (LH1), and
- double clutch device (DK), the double clutch device has：First clutch (K1), for optionally inciting somebody to action described First load stage sun gear (LS1) is coupled on the prestage pinion frame (VC1)；With second clutch (K2), it is used for Optionally the second load stage sun gear (LS2) is coupled on the prestage pinion frame (VC1)；
- wherein the double clutch device (DK) is set in the middle region, and the intermediate region is spatially axially located institute State between prestage speed changer (VG) and the load stage speed changer (LG).
2. planetary gear manual transmission according to claim 1,
Characterized in that,
Power interception is carried out from the load stage speed changer (LG) via the load stage pinion frame (LC1).
3. planetary gear manual transmission according to claim 1 or 2,
Characterized in that,
The planetary gear of the first load stage planetary gearsets (LP1) is radially from interior bonds to the load stage gear ring (LH1) in.
4. the planetary gear manual transmission according at least one in claims 1 to 3,
Characterized in that,
The first load stage planetary gearsets (LP1) and the second load stage planetary gearsets (LP2), which are collectively forming, to be had The planetary classification planetary gearsets of classification.
5. the planetary gear manual transmission according at least one in Claims 1-4,
Characterized in that,
The planetary gear being joined in the load stage gear ring (LH1) of the first load stage planetary gearsets (LP1) has Following pitch diameter, the planetary pitch circle that the pitch diameter is less than the second load stage planetary gearsets (LP2) is straight Footpath.
6. the planetary gear manual transmission according at least one in claim 1 to 5,
Characterized in that,
Provided with axle journal (LW1), the axle journal is interior by the first load stage sun gear (LS1) and the first clutch (K1) Rotor (BK1) is connected, and rotatably arranged with there is hollow shaft (LW2) on the axle journal (LW1), the hollow shaft will be described Second load stage sun gear (LS2) is connected with the second clutch (K2).
7. the planetary gear manual transmission according at least one in claim 1 to 6,
Characterized in that,
Two clutches (K1, K2) are configured to multidisc clutch.
8. the planetary gear manual transmission according at least one in claim 1 to 7,
Characterized in that,
The double clutch (DK) has clutch housing, is connected to the prestage to the clutch housing rotational stiffness (VG) on pinion frame (VC1).
9. the planetary gear manual transmission according at least one in claim 1 to 8,
Characterized in that,
The axle journal (LW1) is felt relieved relative to each other, and to drive first sun gear (LS1) and input shaft, the input shaft drives Move the prestage sun gear (VS1).
10. the planetary gear manual transmission according at least one in claim 1 to 9,
Characterized in that,
The clutch (K1, K2) of the double clutch (DK1) is axially arranged side by side and at least passed through for clutch thin slice Realized using similar component.
CN201710100269.0A 2016-02-23 2017-02-23 High ratio planetary gear shifting transmission Active CN107100965B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016202723.9A DE102016202723B4 (en) 2016-02-23 2016-02-23 High-ratio epicyclic gearbox, in particular for an electrically operated motor vehicle
DE102016202723.9 2016-02-23

Publications (2)

Publication Number Publication Date
CN107100965A true CN107100965A (en) 2017-08-29
CN107100965B CN107100965B (en) 2022-06-03

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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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