WO2015086015A2 - Cvt-getriebe - Google Patents
Cvt-getriebe Download PDFInfo
- Publication number
- WO2015086015A2 WO2015086015A2 PCT/DE2014/200661 DE2014200661W WO2015086015A2 WO 2015086015 A2 WO2015086015 A2 WO 2015086015A2 DE 2014200661 W DE2014200661 W DE 2014200661W WO 2015086015 A2 WO2015086015 A2 WO 2015086015A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- variator
- operating range
- shift stage
- direct shift
- cvt
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by 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
- 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
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
- F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
- F16H37/082—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft and additional planetary reduction 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
- 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
- F16H61/0262—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 hydraulic
- F16H61/0265—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 hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
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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
- F16H61/66—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 specially adapted for continuously variable gearings
- F16H61/662—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 specially adapted for continuously variable gearings with endless flexible members
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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
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/023—CVT's provided with at least two forward and one reverse ratio in a serial arranged sub-transmission
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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
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/025—CVT's in which the ratio coverage is used more than once to produce the overall transmission ratio coverage, e.g. by shift to end of range, then change ratio in sub-transmission and shift CVT through range once again
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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
- F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
-
- 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
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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
- F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three 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
- 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
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
Definitions
- the invention relates to a CVT transmission with a starting element, a variator and with a direct shift stage for switching between the first operating range (low) and a second operating range (high).
- the invention further relates to a method for operating such a CVT transmission.
- CVT is called a continuously variable transmission, wherein the letters CVT for
- Continuously variable transmission stand In order to increase the transmission range of a continuously variable transmission, ie its spread, it is known, for example, from the European patent application EP 2 275 709 A1, to subordinate the continuously variable transmission to a switchable planetary gear.
- the switchable planetary gear allows a two-range circuit and a reverse circuit.
- German published patent application DE 102 61 900 A1 it is known from German published patent application DE 102 61 900 A1 to provide a multi-range CVT with fixed shiftable gears, for example, for starting or for maximum speed, but in the operation of these fixed ratios of the variator is decoupled. Consequently, there is only one stepless area, not all driving areas can be steplessly steered.
- the object of the invention is to simplify the operation of a CVT transmission with a starting element, a variator and with a direct shift stage for switching between a first operating range (low) and a second operating range (high).
- the object is achieved in a CVT transmission with a starting element, a variator and with a direct shift stage for switching between a first operating range (low) and a second operating range (high), characterized in that a maximum transmission ratio of the second operating range (high) of a minimum Gear ratio of the first operating range (low) corresponds.
- Conventional two-range CVT transmissions require a relatively large overlap of the two ranges of transmission to allow comfortable range shifting. Such a large overlap, however, is at the expense of an efficiency-optimized Variatorsp Dr Dahlung in Variator compassion. Due to the inventive Gleichsciens the maximum transmission ratio of the second operating range with the minimum gear ratio of the first Medbe- Rich, the efficiency of the CVT transmission according to the invention can be improved with the direct shift stage.
- the above object is alternatively or additionally achieved in a CVT transmission with a starting element, a variator and a direct shift stage for switching between a first operating range (low) and a second operating range (high), that a minimum variator ratio of the second operating range (high ) is greater than a minimum variator ratio of the first operating range (low).
- the translation ranges are set such that the variator margins which are ineffective regions are not used.
- the variator margin of the second operating range (high) is reduced more than the variator margin of the first operating range (low). It is taken into account that the second operating range (high) normally has a larger transit time component than the first operating range (low).
- a closing valve device is associated with a variator soizidsystem in that the vanator fluid system is closed in a fluid-tight manner by the closing valve device when the direct shift stage is used for driving when the variator is disconnected.
- the variator in particular the variator fluid system, is protected against emptying in a simple manner.
- the invention also relates to a variator fluid system having such a closure valve device.
- the closing valve device preferably comprises a valve which has no or almost no leakage, for example a seat valve.
- the above object is alternatively or additionally solved in a CVT transmission with a starting element, a variator and a direct shift stage for switching between a first operating range (low) and a second operating range (high), that a clutch, in particular a dog clutch, the Direct shift stage, as normally open clutch is executed.
- a clutch in particular a dog clutch
- the Direct shift stage as normally open clutch is executed.
- This can be realized in a simple manner, a safety function against Antriebsbrangverspannen in a system error.
- the dog clutch of the direct shift stage can be designed as a normally open clutch.
- a Starting clutch can be used as a control against Antriebsbrangverspannen when switching the direct shift stage, especially in a time in which the variator and the direct shift stage are simultaneously in the power flow.
- the variator bridging direct shift stage is connected directly to the drive. Due to the direct connection of the direct switching stage to the drive, the direct switching stage can advantageously be used independently of the starting element.
- the direct shift stage may, for example, be connected to a gear used in conventional CVT drive trains to drive a hydraulic pump. Therefore, such a gear is also referred to as impeller.
- the drive comprises an internal combustion engine or an internal combustion engine
- the direct shift stage bridging the variator is driven directly by the internal combustion engine or the internal combustion engine. Due to the direct connection of the direct shift stage to the drive, the direct shift stage in the context of the present invention is preferably used exclusively when driving a motor vehicle equipped with the CVT drive train.
- a further preferred embodiment of the CVT transmission is characterized in that the direct shift stage bridging the variator is connected to a crankshaft with the interposition of a torsional vibration damper.
- a torque of the drive in particular the internal combustion engine or the internal combustion engine, issued.
- the torsional vibration damper is advantageously used to decouple unwanted torsional vibrations, which occur during operation of the drive, in particular of the internal combustion engine or of the internal combustion engine, from the CVT drive train. This prevents unwanted damage in the CVT drivetrain caused by rotational irregularities.
- the partial transmission is, for example, a reduction gear.
- the partial transmission is preferably arranged between a variator output and a differential.
- the direct shift stage is preferably arranged between the starting element and a variator input.
- the partial transmission is designed as a dual-range transmission, in particular as a planetary gear.
- the dual range transmission allows driving in the first range, also referred to as low range, and in the second range, also referred to as high range. In the first area, for example, can be driven with a larger translation than in the second area.
- the designed as a planetary gear dual-range transmission advantageously also allows the representation of a reverse gear.
- the above-mentioned task is alternative or additionally solved in that Variatorrand Schemee the operating areas (low and high) are not used.
- the Variatorrand Geben the CVT transmission has a lower efficiency.
- the variator edge regions which are not used according to the method according to the invention, are preferably lower end regions of the transmission characteristic curves which serve to represent the two operating ranges low and high in a transmission characteristic diagram. In such a translation map, for example, the variator ratio is plotted on an x-axis. The gear ratio is then advantageously plotted on the y-axis of the transmission map.
- the above object is in a method for operating a CVT transmission with a starting element, a variator and with a direct shift stage for switching between a first operating range (low) and a second operating range (high), in particular a previously described CVT transmission, in particular in a previously described method, alternatively or additionally achieved in that is jumped in a quick return adjustment of the gear ratio directly from one operating range in the other operating range, without using the direct shift stage and without completely infinitely back to adjust.
- the ride comfort during operation of the CVT transmission can be improved.
- the above object is alternatively or additionally achieved in a previously described method in that the starting element, in particular a starting clutch, is used as a control against Ver Kunststoffstrangverspannen when switching the direct shift stage. In this case, the starting element, in particular the starting clutch, in particular used in a time in which the variator and the direct shift stage are simultaneously in the power flow.
- the above object is alternatively or additionally achieved in a previously described method in that the starting element, in particular a starting clutch, is used in a slip operation to accelerate the stationary variator before the direct shift stage decoupled and the power flow is directed back to the variator , As a result, the ride comfort during operation of the CVT transmission can be further improved.
- the starting element in particular a starting clutch
- Figure 1 is a simplified representation of a CVT drive train according to the invention in longitudinal section;
- Figure 2 shows the CVT drive train of Figure 1 in cross section
- FIG 3 shows a transmission map of the CVT drive train of Figures 1 and 2 according to a first embodiment of a method according to the invention.
- the CVT drive train 1 includes a drive 3.
- the drive is, for example, an internal combustion engine, which is also referred to as an internal combustion engine when used in a motor vehicle.
- the CVT powertrain 1 is used in automobiles.
- the starting of the motor vehicle is made possible by a starting element 5.
- the starting element 5 transmits a torque from the drive 3 to a starting output part 6. tet.
- the starting starting part 6 is connected via a gear stage with a gear 8 and a gear 9 with a variator input of a variator 10.
- the variator 10 comprises a drive-side conical disk set 11 and a driven-side conical disk set 12.
- the two conical disk sets 1 1, 12 are coupled to one another by an only indicated belt 13.
- the wrapping means 13 is, for example, a special chain.
- the output 15 comprises at least one driven wheel (not shown).
- the output 15 comprises at least two driven wheels.
- a differential gear 16 also referred to as differential 16 is used.
- the differential 16 includes a spur gear 18.
- the spur gear 18 of the differential 18 is in engagement with a Decisionmaschines- gear 19 of a sub-transmission 20.
- the sub-transmission 20 is assigned to a variator output on the drive-side conical disk set 12th
- the drive 3 of the CVT drive train 1 is associated with a torsional vibration damper 22.
- the torsional vibration damper 22 is arranged between the drive 3 and the starting element 5.
- the starting element 5 is designed as a starting clutch 24.
- the starting clutch 24 is a wet-running multi-plate clutch.
- An input part 25 of the torsional vibration damper 22 is rotatably connected to a crankshaft of the drive 3.
- An output part 26 of the torsional vibration damper 22 on the one hand represents an input of the starting clutch 24.
- the output part 26 of the torsional vibration damper 22 is non-rotatably connected to a gear 28.
- the gear 28 is used for example for driving a (not shown) pump. Therefore, the gear 28 is also referred to as a pump gear.
- the gear 28 can also serve to drive another or another vehicle component.
- the gear wheel 28 is associated with a switchable by means of a switching device 29 direct switching stage 30.
- An arrow 31 indicates that the direct shift stage 30 serves to bridge the variator 10.
- the direct switching stage 30 with the aid of the switching device 29 can provide a direct coupling of the gear 18 with the spur gear 18 of the differential 16.
- the drive 3 can be connected via the torsional vibration damper 22, independently of the starting element 5, to the variator 10 via the differential 16 to the output drive 15.
- an axis of rotation of the crankshaft 33 runs perpendicular to the plane of the drawing.
- a circle 34 a rotatably connected to the crankshaft 33 starter ring gear is indicated.
- a radially inner circle represents the gear 8 of Figure 1 represents.
- Another circle represents also referred to as impeller gear 28.
- the gear 8 meshes with the gear 9, which represents the variator input.
- the gear 9 is assigned to the drive-side conical disk set 1 1, which is also shown in Figure 2 as a circle.
- a circle 12 of the output side cone pulley set is indicated.
- the partial gear output gear 19 meshes with the also indicated by a circle spur 18th
- FIG. 2 The circles in Figure 2 illustrate the front-transverse construction.
- the direct shift stage 30 is arranged in FIG. 2 below the crankshaft center 33 and in the direction of the spur gear 18 of the differential 16.
- Front-transverse construction means that the drive 3, in particular the internal combustion engine, and the transmission, here the variator 10 and the partial transmission 20, are arranged side by side in the vehicle transverse direction, for example in front of or above a front axle.
- the partial transmission 20 is designed as a planetary gear with two planetary gear sets and two disc packs.
- the partial transmission 20 designed as a planetary gearbox makes it possible to switch between a first range low and a second range high.
- the partial transmission 20 is used to represent a reverse R.
- FIG. 3 shows a transmission characteristic diagram for the CVT drive train 1 illustrated in FIGS. 1 and 2.
- the translation map is executed as a Cartesian coordinate diagram with an x-axis 51 and a y-axis 52.
- a variator ratio is plotted on the x-axis 51 .
- a gear ratio is plotted on the y-axis 52.
- An upper characteristic curve 53 serves to represent the first operating region, which is also referred to as a low region.
- One under characteristic curve 54 represents the second operating range, which is also referred to as a high range.
- the low range 53 begins at a variator ratio of about 0.65 and a gear ratio of about 4.7.
- the high range begins with a variator ratio of about 0.57 and a gear ratio of about 2.1.
- the direct switching stage which is also referred to as a constant level, for switching between the areas
- the transmission ranges are set such that in the second operating range or transmission range, which is also referred to as a high range, the edge region at the lower end of the characteristic curve 54 is reduced more than the edge region at the lower end of the characteristic curve 53.
- a valve circuit when driving in the direct shift stage 30 and with uncoupled, non-rotating variator 10, a valve circuit is used to protect the variator 10 and a Variatorfizidsystem against idling.
- the valve circuit advantageously comprises a valve which has no or almost no leakage.
- the switching device 29 of the direct switching stage 30 is designed as a dog clutch.
- This jaw clutch is equipped with a normal-open function to represent a safety feature against powertrain distortion in case of system failure. Normally open means that the dog clutch is normally open and actively pressed or closed.
- the starting element 5, in particular the starting clutch 24, is used as a control against stranding during switching of the direct shift stage 30, in particular in a time in which the variator 10 and the direct shift stage 30 are simultaneously in the power flow.
- the starting element 5, in particular the starting clutch 24, is used in a slip mode to accelerate the stationary variator 10 before the direct shift stage 30 is decoupled and the power flow is again directed to the variator 10.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Control Of Transmission Device (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016537978A JP6494628B2 (ja) | 2013-12-09 | 2014-11-28 | Cvt伝動機構 |
DE112014005595.6T DE112014005595A5 (de) | 2013-12-09 | 2014-11-28 | CVT-Getriebe |
CN201480066804.XA CN105793608B (zh) | 2013-12-09 | 2014-11-28 | Cvt变速器 |
US15/103,258 US10167936B2 (en) | 2013-12-09 | 2014-11-28 | CVT transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013225264.1 | 2013-12-09 | ||
DE102013225264 | 2013-12-09 |
Publications (2)
Publication Number | Publication Date |
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WO2015086015A2 true WO2015086015A2 (de) | 2015-06-18 |
WO2015086015A3 WO2015086015A3 (de) | 2015-09-03 |
Family
ID=52596265
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2014/200661 WO2015086015A2 (de) | 2013-12-09 | 2014-11-28 | Cvt-getriebe |
Country Status (5)
Country | Link |
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US (1) | US10167936B2 (de) |
JP (1) | JP6494628B2 (de) |
CN (1) | CN105793608B (de) |
DE (1) | DE112014005595A5 (de) |
WO (1) | WO2015086015A2 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10240667B2 (en) * | 2013-12-09 | 2019-03-26 | Schaeffler Technologies AG & Co. KG | CVT drive train |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE10261990A1 (de) | 2002-03-22 | 2004-02-05 | Audi Ag | Geschwindigkeits-Wechselgetriebe |
EP2275709A1 (de) | 2009-07-15 | 2011-01-19 | JATCO Ltd | Stufenloses Umschlingungsgetriebe |
Family Cites Families (16)
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NL1002245C2 (nl) * | 1996-02-05 | 1997-08-07 | Doornes Transmissie Bv | Continu variabele transmissie. |
US5967931A (en) * | 1998-02-02 | 1999-10-19 | Ford Global Technologies, Inc. | Torodial traction transmission for all wheel vehicles |
JP2000224714A (ja) * | 1999-02-03 | 2000-08-11 | Mitsubishi Motors Corp | 電動機付車両 |
JP2000320630A (ja) * | 1999-05-12 | 2000-11-24 | Fuji Heavy Ind Ltd | 無段変速装置 |
EP2208914B1 (de) * | 2001-05-14 | 2011-11-23 | Nissan Motor Co., Ltd. | Hilfsgetriebe |
JP4715029B2 (ja) * | 2001-05-21 | 2011-07-06 | 日産自動車株式会社 | 変速比無限大無段変速機の変速制御装置 |
DE102004022356B3 (de) * | 2004-04-30 | 2005-12-01 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Toroidgetriebe |
JP2006022839A (ja) * | 2004-07-06 | 2006-01-26 | Nissan Motor Co Ltd | 複合変速機 |
CN101228370B (zh) * | 2005-07-23 | 2013-05-29 | 舍弗勒技术股份两合公司 | 具有变速比可无级调节的多个变速比范围的功率分流式变速器 |
JP2009127843A (ja) * | 2007-11-28 | 2009-06-11 | Toyota Motor Corp | ドグクラッチ及び動力伝達装置 |
US8257216B2 (en) * | 2010-01-14 | 2012-09-04 | Ford Global Technologies, Llc | Infinitely variable transmission |
CN103492751B (zh) * | 2011-01-25 | 2017-11-14 | Dti集团有限公司 | 变速器系统 |
WO2013120655A1 (de) * | 2012-02-14 | 2013-08-22 | Schaeffler Technologies AG & Co. KG | Mehrbereich-cvt |
DE112012006411T5 (de) * | 2012-05-22 | 2015-02-26 | Honda Motor Co., Ltd. | Stufenlos variables Getriebe |
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US9546720B2 (en) * | 2013-04-17 | 2017-01-17 | Ford Global Technologies, Llc | Torque split continually variable transmission |
-
2014
- 2014-11-28 DE DE112014005595.6T patent/DE112014005595A5/de not_active Withdrawn
- 2014-11-28 JP JP2016537978A patent/JP6494628B2/ja not_active Expired - Fee Related
- 2014-11-28 CN CN201480066804.XA patent/CN105793608B/zh active Active
- 2014-11-28 WO PCT/DE2014/200661 patent/WO2015086015A2/de active Application Filing
- 2014-11-28 US US15/103,258 patent/US10167936B2/en not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE10261990A1 (de) | 2002-03-22 | 2004-02-05 | Audi Ag | Geschwindigkeits-Wechselgetriebe |
EP2275709A1 (de) | 2009-07-15 | 2011-01-19 | JATCO Ltd | Stufenloses Umschlingungsgetriebe |
Also Published As
Publication number | Publication date |
---|---|
US20160305521A1 (en) | 2016-10-20 |
US10167936B2 (en) | 2019-01-01 |
JP6494628B2 (ja) | 2019-04-03 |
JP2016540943A (ja) | 2016-12-28 |
CN105793608B (zh) | 2019-09-03 |
WO2015086015A3 (de) | 2015-09-03 |
DE112014005595A5 (de) | 2016-11-03 |
CN105793608A (zh) | 2016-07-20 |
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