EP3973210A1 - Doppelgetriebe - Google Patents
DoppelgetriebeInfo
- Publication number
- EP3973210A1 EP3973210A1 EP20740273.6A EP20740273A EP3973210A1 EP 3973210 A1 EP3973210 A1 EP 3973210A1 EP 20740273 A EP20740273 A EP 20740273A EP 3973210 A1 EP3973210 A1 EP 3973210A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- housing
- transmission
- double
- shaft
- 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.)
- Pending
Links
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/12—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of electric gearing
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
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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
- F16H37/065—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 a plurality of driving or driven shafts
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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
- F16H57/00—General details of gearing
- F16H57/0018—Shaft assemblies for gearings
- F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
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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
- F16H57/00—General details of gearing
- F16H57/0018—Shaft assemblies for gearings
- F16H57/0031—Shaft assemblies for gearings with gearing elements rotatable supported on the shaft
-
- 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
- F16H57/00—General details of gearing
- F16H57/0018—Shaft assemblies for gearings
- F16H57/0037—Special features of coaxial shafts, e.g. relative support thereof
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/027—Gearboxes; Mounting gearing therein characterised by means for venting gearboxes, e.g. air breathers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K7/00—Disposition of motor in, or adjacent to, traction wheel
- B60K2007/0061—Disposition of motor in, or adjacent to, traction wheel the motor axle being parallel to the wheel axle
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2410/00—Constructional features of vehicle sub-units
- B60Y2410/10—Housings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2410/00—Constructional features of vehicle sub-units
- B60Y2410/102—Shaft arrangements; Shaft supports, e.g. bearings
- B60Y2410/1022—Concentric shaft arrangements
Definitions
- the present invention deals with a twin or twin transmission as part of an electric drive train for a vehicle which is equipped with two electric machines, each of which is equipped to drive a wheel after a rotational speed reduction by its own single transmission in the double transmission.
- Such drive trains are sometimes also referred to as tandem motor drive trains.
- a single gear is advantageously a two-stage spur gear with three positions for gear centers in a gear housing.
- the present invention shows a possibility of power and torque transmission in a transmission that is part of an electric drive train.
- the transmission has at least one input shaft and one output shaft, the output shaft being designed for connection of a wheel half-axis such as a cardan shaft.
- the present invention deals with a dual transmission according to the preamble of claim 1.
- the invention also deals with a force and / or torque transmission method by means of a transmission according to the preamble of claim 15.
- Electrically powered vehicles can be designed in such a way that at least two wheels, e.g. B. the two wheels of a rear axle are driven by their own electric motor.
- the electric motor often turns at high speed compared to the desired wheel speed (e.g. up to 15,000 rpm, with higher-speed designs up to 18,000 rpm or even up to 20,000 rpm). For this reason, the speed of the electric motor must be reduced (e.g. by a ratio i between 6 and 9, possibly also by a ratio i in a ratio range from 4 to 12).
- the first electric motor engages an input gear of a first transmission gear in the slow speed.
- the second electric motor engages another, second input gear of a second, different transmission gear in the slow speed.
- the transmission to output shafts which can also be the half-axles of the motor vehicle, takes place over two or more stages. If the two transmissions are installed in a complete transmission housing, then the transmission housing can be attached laterally, ie the first electric motor on a first side and on on the other side of the second electric motor.
- Such gears can be referred to as double gears or also as twin gears, because in the end two completely independent gears are connected to form a larger gear unit. Due to the two existing electric machines, which are usually of the same type, one can also speak of a duo electric machine.
- any controls, in particular with regard to speed and torque, of the connected wheels can be carried out.
- Such a drive train is colloquially referred to as electrical “torque vectoring”.
- torque vectoring In this way, the respective wheel torque at the driven wheels of the motor vehicle can be specified continuously, in particular when cornering, whereby the driving stability of the motor vehicle can be improved and the steering work can be reduced.
- This gearbox category can also be referred to as an active differential.
- These transmissions also increase the efficiency of a motor vehicle drive train. In the case of motor vehicles with only one driving traction motor each, superposition gear types are required for this. Based on the mode of operation, the gears can therefore also be referred to as multiple single wheel gears.
- the twin gearbox is designed to drive two road wheels independently. By rotating the output shafts of the transmission, a direction of travel of the vehicle, advantageously with a passenger compartment, z. B. a car or a truck such as a small truck or van, by determining the rotation of the at least two wheels.
- WO 2016/147 865 A1 (applicant: NTN TOYO BEARING CO LTD .; Disclosure date: 09/22/2016) in numerous figures a possible drive train with two electric machines and two half-axes, so that in the presented drive train each electric machine is intended to drive a half-axis. Relative relationships or arrangements of axes of individual gear wheels of the transmission can be seen from some figures. Accordingly, a drive train shown in WO 2016/147 865 A1 was designed, the highest axis of which should be the drive shaft axis, while an axis interposed between the drive gear and the output gear occupies a middle position. The motors should be placed in front of the rear axle.
- EP 2 310 220 B1 would therefore like to provide the entire drive unit with a single overall housing around this drive unit.
- the electric motors are also part of the transmission.
- Such designs should work for system suppliers who want to design their entire drive unit as an exchange and possibly also as a disposable product.
- DE 100 54 759 B4 (patent holder: ZF Friedrichshafen AG; date of issue: October 29, 2009) and WO 2005/008 098 A1 (applicant: DaimlerChrysler AG; date of publication: January 27, 2005) recommend two or three tapered roller bearings between two shafts, which are combined to form a double shaft of a double clutch transmission, to be provided as their bearings, because this type of bearing should be able to absorb radial forces and axial forces in a particularly compact manner.
- double clutch transmissions it is common to switch two or more than two drive sources present on the input side alternately to one of the two input shafts of the transmission.
- JP 2018-039 396 A (applicant: NTN CORP; publication date March 15, 2018) deals with a two-engine motor vehicle drive that is similar to the drive of US 2018/0 015 815 A1. In such a drive there should be a seal between the oil-filled gearbox and the electric motors. JP 2018-039 396 A also describes some aspects of their overall oiling system.
- JP H051-16 542 A (applicant: AISIN AW CO LTD; publication date: May 14, 1993) describes a system with several motors, the heat capacity of each motor being increased.
- the cooling can be done, for example, by oil, which is to flow in channels through the motor windings and is to be circulated by a pump.
- DE 10 2009 018 786 A1 presents a so-called fluid ring in fluid or oil lubrication of a transmission.
- oil should be lubricated by entrained fluid or oil.
- FIG. 2 of DE 10 2009 018 786 A1 a ventilation duct is shown, through which, if possible, no oil should escape, even in the event of a pressure increase.
- the fluid ring is intended to take on the function of a shielding ring which can intercept fluid thrown directly in the direction of the ventilation duct.
- at least one side wall of the fluid ring can be provided with at least one opening.
- a kind of “labyrinth” is to be created to slow down the fluid so that it can then flow off in an annular groove in the fluid ring.
- the Japanese patent application JP 2016 175 563 A (applicant: NTN TOYO BEARING CO LTD; publication date: October 6, 2016) describes a drive unit that has two electric motors and a double gear. An air flow is guided through a wing-like air guide arrangement for air cooling onto a gear housing. This is intended to improve air cooling of the reduction gear. The air flow does not seem to affect the interior of the gear housing.
- the Japanese utility model JP H05-32 863 U (owner: MITSUBISHI HEAVY IND LTD; publication date: 04/30/1993) deals with a ventilation chamber, which is adjoined by a bulge or wall opening in a housing.
- US patent application US 2017/0 002 919 A1 (applicant: DEERE &COMPANY; publication date: 05.01.2017) deals with a transmission for a tractor, for which a ventilation pipe system is described.
- a ventilation tube that can be seen in FIG. 4 of US 2017/0 002 919 A1 opens on the other side into a raised area - better seen in FIGS. 5, 6 and 7. Rotation of the input shaft is said to help reduce the amount of lubricant leaking out of the gearbox by centrifugally driving lubricant towards the wall of the vent tube.
- the patent application DE 41 36 392 A1 (applicant: Harnischnostir Corp .; publication date: 07.05.1992) shows, in three exemplary embodiments, gear drives that are to be installed in an open pit excavator.
- a variant can only be seen in FIGS. 9 and 10, in which a housing ventilation connection is attached in a ventilation cover at a point in the alignment of which a shaft and a gear can be found.
- FIG. 10 shows a deflected housing ventilation nozzle.
- EP 2 332 760 A1 (applicant: KANZAKI KOKYUKOKI MFG. CO. LTD; publication date: June 15, 2011) describes an electric drive unit with two electric motors for a vehicle axle. Each unit consisting of an electric motor and a transmission is there to be connected to a wheel.
- a ventilation pipe extends between two half-shells of housings of different motor units.
- a ball check valve can be located on one connection side of the vent pipe.
- the gears each have three shafts that are not allowed to interact with the ventilation pipe.
- a Ravigneaux planetary gear is described as part of a power transmission device that includes a hydraulic torque converter.
- a ventilation line and a breathing chamber, which are to be formed in the countershaft, should be provided in such a transmission.
- the countershaft should run parallel to the output shaft and be rotatably supported in a gear housing via a pair of bearings.
- the countershaft carries a final drive gear which - as the name suggests - is formed on a first end side of the countershaft.
- a differential ring gear which meshes with the pinion gear and which is coupled to the differential mechanism is arranged at the other end of the countershaft. Hydraulic oil should be used as the lubricating / cooling medium in such a transmission. An undesired drainage of oil from the breathing chamber should be prevented by a ventilation line.
- the first embodiment refers to a separate ventilation pipe made of plastic.
- DE 10 2015 105 243 A1 it is proposed to seal the ventilation pipe with an O-ring that sits in an annular groove of the ventilation pipe with respect to an inner surface of a sleeve-shaped housing section.
- Details of the ventilation can be seen in particular from FIG. FIGS. 4 to 6 deal with the details of a first duct section of the ventilation and, among other things, introduce projections which are incorporated into the duct to break oil foam bubbles.
- An integral transmission described in DE 10 2013 208 564 A1 (applicant: Voith Patent GmbH; filing date: May 8, 2013) should be part of a transmission compressor run.
- Such a transmission should have a drive gear connected to a drive shaft in a rotationally test manner, an axis of rotation of the drive gear being arranged in an arrangement plane with an axis of rotation of the output gear. Between these two gears there is a large wheel which is in engagement with both gears and whose axis of rotation is vertically offset with respect to the plane of arrangement.
- Each output gear is connected to two compressors. The aim is to achieve an optimal load distribution.
- DE 10 2013 208 564 A1 suggests designing the gears with helical teeth.
- the exemplary embodiments presented in DE 10 2013 208 564 A1 deal with providing a second output gear in addition to a first gear, the axis of rotation of which is also located in the plane of arrangement.
- a steam turbine is provided as the drive.
- two output gears are driven by an electric machine in one embodiment. A combination of these different drive units on the transmission is also proposed.
- a shaft carries the gear called “idler gear”, which meshes with the rotor shaft gear and with a so-called first gear.
- These three shaft axes are intended to be arranged in accordance with the arrangement shown in FIG. 3 in a common plane which extends perpendicular to the axes.
- the second gear should be in mesh with the output gear.
- the second gear and the first gear should therefore form a double gear.
- the shafts should be continuous for the two sub-transmissions and be supported in the peripheral area on the housing so that the gears arranged on them can rotate independently of one another.
- a vehicle is used in the document described, which is supposed to represent an inverting pendulum.
- a left and a right drive unit are attached to the side of the central axis.
- Each of these drive units drives a pulley via a belt drive.
- the drive unit is located above the main wheel of the vehicle.
- a battery attached to the vehicle frame is used to supply power to the drive units.
- the drive units are arranged under a seat which is intended to accommodate a single person.
- the seat is on a frame that is supported by a rear support wheel.
- the very detailed patent application also shows in FIG. 3 a rotor shaft, an intermediate shaft and an output shaft of the drive unit. As can be seen from FIGS. 6 and 7, these three shafts are rotatably mounted separately for each partial transmission in the housing wall and in an intermediate wall.
- the intermediate shaft is shown positioned higher than the other two shafts, with the output shaft occupying the lowest position.
- US 2018/0 141 423 A1 (applicant: NTN Corporation; filing date: April 18, 2016) deals with transverse forces, especially in the second shaft of a double transmission comprising three shafts, which therefore has two sub-transmissions. As shown in FIG. 4, lateral forces are minimized by helical gears running in opposite directions in the gear pairs to and from the second shaft. In Figures 1, 6 and 7, input shafts that are supported at both of their ends and are not nested with their adjacent shaft, are shown. Furthermore, the transmission according to US 2018/0 141 423 A1 has a support structure.
- the object according to the invention is achieved by a double transmission according to claim 1.
- the object of the invention is achieved by a force and / or
- the gears which are used in particular as so-called reduction gears, i.e. H. as a gear with a translation into the slow speed, are parts of electrical drive trains should be designed so that, especially with regard to the limited electrical storage options in motor vehicle construction, as much as possible of the electrical energy is available for the drive, i.e. This means that as little electrical energy as possible should be "used” for auxiliary units, other tasks or through power losses.
- torque vectoring The advantages of “torque vectoring” come into play in vehicles that can drive forward at medium and high speeds. Medium speeds can be settled at speeds of more than 25 kilometers / hour. Particularly high speeds are more than 200 kilometers / hour, e.g. B. at 250 kilometers / hour.
- motor vehicles preferably have all-round protection for a driver, such as a passenger cell or a cabin.
- the cabin offers an interior space in which at least one person, preferably several passengers, can stay when driving the vehicle.
- a passenger cell is usually a safety passenger cell, which is a protective space in the event of a collision.
- a passenger cell is advantageously designed as a protective space against environmental influences such as lightning, in particular in that the chassis forms a Faraday cage.
- the two (sub) gears or single gears of the double gear are rotationally largely independent torque transmission units, especially in the case that an effective coupling via a wheel that can be driven by the (sub) gear via a travel path is not taken into account.
- the individual gears are combined as a structural unit to form a double gear.
- the input shafts of the double transmission according to the invention and the output shafts of the double transmission are arranged in a central area, based on an extension transverse to a direction of travel, i.e. in particular a shorter distance from one housing wall to an opposite housing wall of the transmission housing, in particular lying at the same height .
- the input shafts and the output shafts define a reference plane within the transmission housing.
- the reference plane is a (essentially) flat surface that is spanned between the input shafts and the output shafts. If the reference plane is compared with the course of a floor, either of the transmission housing or a flat road, the reference plane preferably extends parallel to a flat travel path.
- the reference plane is advantageously fixed in an installed state of the double transmission or the intended installation position. It can also be said that a reference plane extends in a (essentially) parallel arrangement in comparison to a plane spanned by four wheel carriers on which four road wheels of the motor vehicle are attached.
- the inclination between the reference plane and the spanned plane is preferably less than 10 °, in particular less than 5 °.
- the position of the input shafts and the output shafts of the double transmission results in the reference plane as an (imaginary) geometric configuration within the transmission housing.
- the gear case offers multiple positions for gear centers. Two positions for gear centers are occupied by the drive shaft (s) and the output shaft (s). A first position is occupied by two input shafts of the double transmission. One position for gear centers is occupied by the two output shafts. Between the first position and the second position there is a middle or third position that is not aligned with the other two positions.
- This position of a central axis of one of the gearwheel centers is angled to the reference plane as a position remote from the transmission housing. It is also possible to speak of a ridge-like arrangement of the central axis opposite an attic-like level. This increase in the position of the central axis relative to the reference plane results in an overall axis arrangement of all gearwheel centers in the manner of a triangle.
- a first side preferably a long side, like a hypotenuse, is preferably made to coincide with the reference plane.
- a second side and a third side preferably form two short sides, each intersecting the first side, in particular at one end of the first side, each a straight line, like two legs or like an opposite cathetus and an adjacent cathetus.
- Straight lines that follow the short pages opposite the first page intersect with a slope in a value that can be taken from the angular range between about 5 ° and 70 ° Reference plane or the first side.
- the second side and the third side can each form an (imaginary) corner with an angle with the first side. It is advantageous if an angle is selected from an angle range between 10 ° and 50 °. Div. Mathematical simulations and calculations have led to the fact that angles appear particularly advantageous which lie in an angle range between 15 ° and 48 °.
- the central axis can be cut by a straight line which is guided to the central axis from one of the remaining gear centers, that is to say the gear centers lying laterally to the central gear center.
- An angle that can be removed between the reference plane and the straight line is an angle from the angular range between 5 ° and 70 °, in particular between 10 ° and 50 ° and very preferably between 15 ° and 48 °.
- the middle axis can be cut by means of a straight line that can be formed to one of the gear centers (conceptual or fictitious). This straight line deviates from the reference plane.
- the deviation can be expressed by an angle which is taken from an angle range between 5 ° and 70 °, in particular between 10 ° and 50 ° and very preferably between 15 ° and 48 °.
- An advantageous angle range can also be between 23 ° and 70 °. Outside advantageous angle ranges z. B. more than 70 ° or less than 5 °, some advantages of a triangular arrangement of the axes are hardly significant.
- the arrangement of the axes of the gear centers advantageously forms an upside-down "V", of which the respective input shaft and the output shaft with their shaft longitudinal axes, provided that the transmission housing is installed in a preferred installation position in the motor vehicle (in about) describe a horizontal plane.
- the electrical machines (operated as electric motors in the mode of operation considered here) that act on the input shafts and drive the input shafts with their individual weights (due to their components made of copper) can be mounted in the motor vehicle at a height (viewed from a street) that corresponds to the position or the height (viewed from the street) of the output shafts. In particular, this results in more stable cornering behavior with a compact housing design in the longitudinal direction of the transmission housing.
- the spaced-apart arrangement of the electrical machines increases the total torque that has to be applied by acceleration forces when cornering in order to increase lateral inclination of the motor vehicle.
- the compact design in the longitudinal direction creates additional installation space for accommodating electrochemical energy stores, which for safety reasons are preferably installed in the middle of the motor vehicle. If a focus of the motor vehicle is to be placed particularly low, z. B. in racing or sporty road vehicles, a "V" -shaped arrangement of gear centers for a double transmission can be used.
- the transmission housing is preferably installed in the motor vehicle with its housing longitudinal direction or housing longitudinal axis along a vehicle longitudinal axis, in particular parallel to this, preferably even on the vehicle central longitudinal axis.
- the input shafts and the output shafts extend transversely to the longitudinal direction of the housing, so preferably form an angle of approximately 90 ° with the longitudinal direction of the housing.
- the force and the torque can be transmitted from the respective input shaft to the output shaft via spur gear pairs.
- a (first) drive power is brought to a first side of the transmission by a first electric machine.
- a second drive power is brought to a second side of the transmission by a second electric machine.
- Each of the two sub-transmissions can be operated independently of the other sub-transmission.
- Both partial transmissions are preferably arranged in mirror image to one another. It is thus possible to arrange two spur gears in mirror image on the intermediate spur gear bearing and to support them.
- the two shafts of a sub-transmission, the input shaft and the output shaft, are located or arranged with their shaft centers on a uniform level or on a uniform level, which can also be referred to as a plateau.
- the gear or the gears on the spur gear intermediate bearing represent a deflection stage or several deflection stages for a torque.
- At least one freewheel body is arranged on the axle so that the spur gear can be viewed as a loose gear.
- several freewheel bodies such as. B. four freewheel body available.
- the angular arrangement then contributes to the fact that introduced and discharged forces at least partially compensate each other. In this way, transverse forces can be compensated for, in particular when the train is running.
- the central axis can be arranged to the gearwheel centers of the gearwheel on the input and output shaft side so that a straight line between a gear center and the central axis is to be formed at an angle.
- the angle has a value that is taken from an angle range of 5 ° to 65 ° to the reference plane is.
- the central axis can also advantageously be positioned in the gear housing in such a way that a straight line between a gear wheel center and the central axis assumes an angle that is taken from an angular range of 15 ° to 48 ° to the reference plane.
- the double gear with its arrangement of the axes of the gear centers and the respective gear rotatably arranged on the relevant gear center is advantageously constructed in such a way that a driven gear, which is designed for rotation about the central axis, has a direction of rotation turning away from the housing bottom of the gear housing Gear wheel contact with an upstream gear wheel, d. H. so has in a driving way.
- a driven gear which is designed for rotation about the central axis
- This not only has an advantage with regard to the force compensation, but can also advantageously produce a lubricating film formation of an oil film drawn from the sump in a crashing transmission.
- the transmission is designed for a preferred direction of travel. In the operating mode of the pulling operation of the transmission, after contact between the driving gear and a gear on a central axis, the central gear is rotated away from the housing base.
- the middle gear initially moves in the preferred direction of travel.
- the middle position is formed by a (stationary) axis, in particular an axis fixed to the housing, and not by a shaft.
- a (stationary) axis in particular an axis fixed to the housing, and not by a shaft.
- Such an axis which is arranged non-rotatably in the transmission housing, with idler gears rotatably arranged thereon, offers the advantage that the transmission housing can thereby be stiffened without having to provide additional components for this purpose.
- the cover-like transmission housing parts connected to the axle also tend less to emit structure-borne noise over a large area, since in particular resonances can be avoided.
- a stationary axis When a stationary axis is spoken of, what is meant in particular is an elongated component that is statically arranged in relation to the gearbox housing and that is designed in an axis-like manner.
- an axis In a constructive sense, an axis is used when it comes to a component, less only an (imaginary) axis line is addressed.
- An axle can therefore be a force-absorbing component of the transmission.
- One axis has a cross section. The axis is particularly rotationally fixed with respect to the gear housing, preferably fixed to the Gear housing connected, is arranged.
- the axes in particular all gear wheels, can extend (essentially) orthogonally to a connection plane that lies between two housing parts.
- a connection plane is located where there is a transition through the edge areas of the housing parts and which bear against one another when the gearbox is in an assembled state.
- at least one, preferably all, axes cross the connection plane in a longitudinal direction of the axes.
- the connection plane which is present in the form of a ring on a housing wall, lies outside the assembly area of a shaft or an axle.
- the axes or shafts can be supported or positioned on the housing in a particularly reliable manner if these shafts, each with an end region, are assigned to exactly one housing part.
- the input shafts and the output shafts are, as the selected term “shaft” already indicates, rotatable components that are mounted in the gear housing by floating bearings and / or fixed bearings. In this way, the power flow into or out of the double transmission can be brought about in a simple manner.
- An input gear and the input shaft can be integrally formed.
- An output gear or output gear and the output shaft can be formed in one piece.
- Two shafts, in particular the output shafts and the input shafts, are advantageously arranged in a line, it can also be said to be in alignment, one behind the other. This enables inter alia the particularly compact design of the entire transmission.
- the gearwheels rotatably mounted on the central axis are preferably designed as stepped gearwheels which preferably have a larger, first diameter on the input shaft side or the motorized drive side.
- the step gears are preferably stepped towards the output shaft side; in this case they have a smaller, second diameter. In this way, a desired reduction can be implemented with little space requirement.
- the power flow in the transmission can also be at least partially compensated in this way. The power flow is realized with low losses.
- the reduction or transmission to slow speed is effected by the fact that the double transmission in a first stage (intermediate stage) is based on the arrangement of the three gear centers, or the arrangement of the longitudinal axes of the input shaft, the output shaft and the stationary axis for the middle position, like an upside down "V", one of that Carries out translation facing away from the housing bottom of the gearbox housing and, through its second stage (intermediate stage), causes a translation facing towards the housing bottom.
- a translation facing towards or away means that the translation is connected to a direction of rotation around the gear centers, which, in particular from a gear engagement area, is directed towards the housing base or away from the housing base.
- this type of construction turned out to be the type of construction that enables particularly low-jerk operation of the double transmission during load changes.
- the teeth of the gears on the central axis are designed so that the meshing of the gears installed in the transmission are free of transverse forces. If there is talk of freedom from transverse forces, this does not rule out the possibility that transverse forces can occasionally occur in operating situations. In other words, a permanent load due to transverse forces in the gears with the helical gears is as low as possible.
- the helix angles of the teeth on the gear in the middle position, so that these gears have helical teeth can be designed with helical angles that are aligned with one another.
- the helix angles of both toothing areas of a double or stepped gear (for the middle position in the gearbox structure) preferably have the same sign.
- a common, identical "sign" expresses that with reference to a uniform direction of the axis of rotation or gear side, an inclined position of the teeth, in particular along a gear circumference, in a same tangential direction away from the axis of rotation.
- the inclinations of the teeth on a first gear wheel and a second gear wheel, these being gear wheels arranged non-rotatably with respect to one another, are ideally in the same direction, i.e. H.
- first and second row of teeth of the double or step gear that are aligned next to one another and one on the other.
- the helix angles of the first and second row of teeth can be different from one another.
- the helix angles are preferably set in relation to each other in such a way that despite different pitch circle diameters of the gears, a transverse force of approximately the same magnitude, but opposite, results from each of the two sub-gear stages, which are formed with the double or stage gear.
- the value of the individual helix angles z. B. advantageously set by a calculation method.
- a favorable ratio of two helix angles to one another is present when the transverse forces formed by two gear wheel stages, ie in particular forces based on the helix angle in the approach cathode, largely cancel each other out.
- the helix angle b ⁇ of the first stage and the helix angle ß 2 of the second stage can, for. B. for specified gear wheel diameters d 2 , d 3 can be determined using the following formula:
- the term “tan” describes the tangent of the respective angle.
- the angles ß ⁇ ß 2 are based on a straight line as a construction aid, which rests on a tooth of the gearwheel parallel to the axis of rotation.
- the diameters d 2 and d 3 are the diameter of the gears of the stepped gear, the diameter d 2 being assigned to the first stage or first reduction stage of a single gear and the diameter d 3 to the second stage or second reduction stage of the individual gear.
- the stages preferably comprise further gears, e.g. B. an input gear with a diameter in the first stage and a driven gear with diameter d 4 in the second stage.
- the diameter d 2 can also be referred to as the pitch circle diameter of the larger gear wheel of the step gear and the diameter d 3 as the pitch circle diameter of the smaller gear wheel of the step gear wheel or of the stepped pinion of the step gear wheel.
- the first stage or stage 1 - viewed in the direction of the torque flow - is closer to the drive motor. It can be called an entry level.
- the second stage or stage 2 is - viewed in the direction of torque flow - closer to the output or the road wheel than the first stage.
- the term reduction stage is based on the assumption of a torque flow direction viewed from the drive motor.
- the ratio of the tangent of the helix angle of the second stage to the tangent of the helix angle of the first stage is (almost) identical to the ratio of the diameter of the gearwheel involved in the first stage to the diameter of the gear of the step gear involved in the second stage.
- a single transmission is considered here. In this way, possible transverse forces on the step wheel of a working individual transmission or both identically designed individual transmissions largely cancel each other out. If the same size or an identical ratio is used when forming the ratio, deviations due to customary manufacturing tolerances are not taken into account. The same size or an identical ratio can also be understood to mean deviations which are less than 20% of a ratio from the above formula. Preferably, the transverse forces are eliminated at least for parts which amount to more than 20% of the possible transverse force in a single step.
- friction effects more precisely those friction effects in tooth meshing areas, can also be taken into account, whereby an even better compensation of transverse forces is possible.
- Possible tilting forces whose moment strength includes the width of the double or stepped gear, can be reduced - also greatly - by the ratio of the helix angles.
- gears In operation, no or only slight axial forces occur on such gears in relation to the bearings of the gearwheels, so that this constructive measure has a favorable effect on the power loss of the double gear.
- helical gears guarantee particularly low-noise operation of a transmission. Such gears also enable the transmission of higher powers with less space requirement, since several teeth are always in mesh.
- the gear wheels arranged on the axle are mounted on the axle with suitable bearings, in particular in the form of needle bearings or roller bearings with or without an axial support function.
- suitable bearings in particular in the form of needle bearings or roller bearings with or without an axial support function.
- needle roller bearings in particular ensures that the gear wheels are supported without tilting and that their toothing has less friction with one another.
- a sleeve for mounting the gearwheels arranged on the axle which sleeve has an air guiding structure which extends out of the gearbox housing and which can be used to vent the gearbox housing.
- a first (partial) transmission and a second (partial) transmission are preferably adjacent to one another. They have (essentially) identical, but at least almost identical or highly similar structures with regard to their gear ratios, their gears, the arrangement of the gears, the resulting overall gear ratio and the arrangement and mounting of the individual gears.
- the (overall) transmission can thus be viewed as a pairing of two (partial) transmissions, so that the (overall) transmission can be referred to as a twin transmission.
- the twin gearbox is provided for connecting two input drive machines, in particular electric motors or electric machines, via the gearbox to two semiaxes arranged on the output side of the gearbox, such as. B. to connect two cardan shafts for a connection to a road bike.
- the twin gearbox has a double input shaft to which both electric motors can be connected.
- the two (sub) transmissions of the twin gear are rotationally largely independent of each other torque transmission units, especially in the case that an effective coupling via a travel path via a wheel that can be driven by the (sub) transmission is not taken into account.
- the motor vehicle drive train to which the twin transmission belongs, is a drive train which, as stated, is to be driven by electric motors. At least two electric motors are connected to the twin gearbox.
- each electric motor drives a road bike assigned to it.
- the electric motor is advantageously responsible for driving a single road wheel.
- the torque of the electric motor is switched through or transmitted via a (partial) gearbox of the twin gearbox to a single wheel for driving the single wheel of the motor vehicle.
- the input shaft of the twin transmission is designed as a double input shaft so that a separate electric machine can be connected to each side of the transmission. Consequently, one speaks of a (pure) electric drive of the motor vehicle when the drive train described here is dealt with together with the transmission.
- the double input shaft is designed for the connection of two separately operated motors.
- the double input shaft offers connections for two motors.
- the twin gearbox is designed with its double input shaft in such a way that two (separately working) gear ratios can be derived from the double input shaft.
- the double input shaft has two first gear wheels, which can be placed in the middle of the double input shaft, preferably designed as part of the double input shaft.
- the translation or the two translations of the first two gears are formed by the combination with two second gears of the twin gear.
- the first gears are located next to each other, one gear on each input shaft.
- Each input shaft has its own first gear.
- the first two gears are arranged in the center or in a central area of the double input shaft.
- the input gear and input shaft can be formed in one piece.
- the two first gears are each located in the area of one end of each individual input shaft. It is even more advantageous for a precisely guided or supported input shaft and in particular for load distribution over several input shaft bearings if the end region of at least one of the individual input shafts comprises an extending journal region, the extension being less than two and a half times the width of the first gear over a gear wheel of the first gear protrudes, preferably in the direction of the second single input shaft.
- the journal area can in particular protrude into a journal receptacle of the second input shaft.
- the double input wave is a wave that is composed of two waves that are shifted into one another.
- the double input shaft can also be referred to as a shaft that is nested in one another in some areas.
- the two individual input shafts are (conceptually) pushed towards one another.
- one input shaft is the partly outer shaft that offers a central cavity area into which the other input shaft projects.
- Such a double input shaft is designed as a partially nested, intermeshing shaft in such a way that a motor can be connected to each individual shaft.
- each individual input shaft is designed to be self-supporting at its end. Another term for such a wave is piloted wave.
- the design of the input shaft is particularly compact if the first gears that protrude from the input shaft are so close to one another that over the space between the two first gears (in the end) only from a separating air gap between the gear troughs can be talked about.
- a support structure can be arranged in this.
- the double input shaft is supported several times within a housing of the transmission. It has turned out to be particularly advantageous if the double input shaft is supported a total of four times. In this case, each single input shaft can be supported twice with respect to the housing and as a result the double input shaft is supported four times with respect to the gearbox housing.
- the double input shaft with shaft sections or partial shafts pushed into one another i. That is, by interleaving the single input shafts and by forming a double input shaft, a twin gearbox is made possible that is extremely narrow in its input area.
- the gears which can be part of the input shafts, are placed in the center of the double input shaft as far as possible, the thickest shaft design of the double input shaft is to be found in the area that was only created by the placement of the gears.
- the double input shaft composed of two single input shafts has a first end and a second end. Both ends of the dual input shaft can be referred to as extremities because these ends protrude from the transmission housing.
- the extremities are designed as connection points for non-positive connections.
- a drive can be connected to the twin gear via this.
- the extremities are intended for drive couplings.
- Favorable profiles for the coupling of drives to the double input shafts are e.g. B. splines. If splined shaft profiles are incorporated into the extremities, then non-positive connections can be implemented on the shaft jacket and / or shaft face of an input shaft. In addition to splined shaft profiles, other profiles are also available.
- groove structures can be incorporated into the extremities of the double input shaft, so that a toothed engagement of a separate drive on each Extremity can take place.
- a toothed engagement of two corrugated profiles in one another can also be referred to as a positive connection.
- a form fit enables a torque to be transmitted from a shaft to a shaft connected to it, such as a motor shaft and an input shaft.
- the torque is preferably transmitted between a shaft jacket and a shaft end profile, which can also be referred to as a shaft core, in particular the shaft jacket on a first shaft or partial shaft and the shaft core on a second shaft or partial shaft, preferably on their profiled extremities intended for a connection , is available.
- the shaft jacket has a smaller diameter than the shaft core.
- a drive enclosure can be formed by connecting the shaft jacket and shaft core. If both extremities are shaped with a profile as a shaft core, a non-positive and / or form-fitting connection of the drive to the input shaft can be created with a shaft jacket designed separately as a sleeve.
- the housing of the transmission advantageously has several fastening points. Some of the attachment points can be used to connect prime movers. Two electric machines to be attached to the gearbox in a force-locking manner via end flanges can form a block-like unit with the twin gearbox by screwing them on (or any other suitable fastening method).
- the twin gear is particularly compact if the double input shaft is designed as a particularly short shaft.
- a short input wave can be achieved with stub waves.
- the double input shaft can be produced by two stub shafts aligned along an axis. Here, the stubs of the stub shaft are oriented in opposite directions. The stubs of the stub shafts terminate the double input shaft in opposite directions.
- the respective stub shaft advantageously diverges outward at its end facing away from the stub.
- This foundation-like design of the stub shaft can be used to work a rotating ring gear integrally into the bottom of the stub shaft.
- a ring gear can also represent the drive gear.
- the widest diameter of the stub shaft would be that which merges into the drive gear or represents this.
- connection that is to be established between one of the drive machines and the double input shaft for the transmission of the drive can be achieved by means of a drive enclosure.
- the double input shaft has support points.
- Each part of the double input shaft intended for a drive has two bearings beyond its drive enclosure. These two bearings are supported on parts of the housing of the twin gearbox.
- the double input shaft is advantageously an oil-lubricated shaft.
- the double input shaft can be designed as a stepped shaft.
- the oil lubrication is carried out in such a way that excess oil (too much oil) can be collected in a housing pan.
- the oil from the housing pan is first fed directly to the rolling bearings, which can be exposed to high loads.
- the transmission has two housing troughs.
- the double input shaft lubricates opposite two housing pans or with the oil from two housing pans.
- a widest diameter is advantageously in the area of a center of the double input shaft composed of two single input shafts.
- the two gears of the double input shaft are supplied with oil from lower-lying gears, transferred from tooth to tooth from the sump.
- the oil is distributed depending on the speed by oil splashes or oil mist.
- bearings arranged outwards are ball bearings. Lateral migration of one or the other shaft of the double input shaft can be blocked by a stop on the ball bearings on the double input shaft and on a housing part of the twin gear.
- the bearings of the double input shaft can be paired with two bearings each.
- a deep groove ball bearing and a cylindrical roller bearing are combined side by side. This makes it possible for a deep groove ball bearing and a cylindrical roller bearing to center a half-shaft or a single input shaft with respect to the housing of the twin gear.
- Two bearings each, with a deep groove ball bearing and a cylindrical roller bearing preferably being present, can center one of the two shaft-like parts of the double input shaft in relation to the twin gear through their combinations arranged next to one another.
- the cylindrical roller bearing is preferably located next to the ring gear or the output gear of the stub shaft.
- the deep groove ball bearing preferably delimits the cylindrical roller bearing laterally.
- the nested two parts of the double input shaft that is to say the single input shafts, are limited to prevent sideways movement by their outer groove ball bearings.
- the output via the respective output gear leads to predominantly radial loads in the largest part or the part with the largest diameter.
- inner bearings In addition to the outer bearings of the double input shaft, there are also inner bearings.
- the inner bearings can also be referred to as double input shaft bearings to distinguish them from the outer bearings, among other things because the inner input shaft in a radial direction over the inner bearing and a first outer bearing and preferably a second outer bearing of the outer input shaft against the Gear housing is supported.
- the inner bearing can also be designed as a double bearing. It is also possible that both outer bearings, as already explained, are each designed as double bearings.
- the fact that there is an inner and an outer input shaft does not mean that it is a known concentric hollow shaft configuration, because an overlap area of the two shafts is preferably less than half, in particular less than a third of the length of the double input shaft.
- the bearings arranged inside the double input shaft i. H. the bearings between the two single input shafts can be designed as plain bearings.
- Each slide bearing advantageously has a different diameter than the other slide bearing.
- the interengaging shafts can be supported against one another.
- the sliding bearings are advantageously arranged in a relative relation to the outer bearings. In fact, it is possible to position at least one of the sliding bearings below a paired arrangement of two outer bearings. The at least one slide bearing is aligned in the area of the two outer bearings. The plain bearing is thus arranged within the outer bearing. In particular, it is possible to position a slide bearing under two outer bearings.
- Needle roller bearings generally run with less friction than plain bearings. Needle bearings can be arranged in the same way as was previously described for the plain bearings. An arrangement of two needle bearings next to one another is favorable for load distribution and, in particular, for bearing lubrication.
- a first needle bearing can be located near the gearwheel cheek between the journal and the journal receptacle.
- a second needle bearing is preferably assigned to an end region of the journal. The end area of the pin is located at an air gap between a pin end face and a pin receiving base.
- Groove-like recesses for the needle roller bearings in particular the radially arranged, inner running surfaces, can be incorporated into the journal of the needle bearing.
- An outer running surface - seen radially - preferably offers a cylindrical inner wall of the pin receptacle.
- the needle bearings or plain bearings can be lubricated with oil through at least one oil guide bore in the double input shaft.
- An oil guide hole can z. B. extend in at least one of the individual input shafts and open into an air gap in the pin receptacle, which can also be referred to as the oiling gap.
- At least one oil guide bore preferably starts from an oiling space in the vicinity of a deep groove ball bearing of the individual input shafts, which is likewise supplied with oil.
- the double gear whose gear housing can be based on two half-shells, inside each of which an independent gear is realized, is a paired gear or paired gear, i.e. H. built almost like twins; Another term for this is twin gear.
- twin gear is part of a motor vehicle drive train.
- the motor vehicle drive train includes two electric machines. Using the transmission, each electric machine is provided to drive a road wheel assigned to the respective electric machine. An electric machine provides the torque flow to one of the road wheels using half of the transmission.
- the transmission includes gears, in particular spur gears, and roller bearings that are to be lubricated by means of an oil film.
- the gears and roller bearings are located inside one of the sub-housings.
- the oil lubrication is preferably carried out passively, i. In other words, the oil film is distributed by means of a rotary distribution by means of gear wheels (slipping). It can also be said that the gears pull the oil film with them. After a (longer) standstill, the oil film is gradually distributed over all gears and roller bearings, in particular through a new build-up of the oil film.
- the gears and roller bearings are designed for oil lubrication. The oil lubrication takes place inside the gearbox housing.
- the gearbox is not completely filled with oil, but the total available volume (in each sub-gearbox) is greater than the volume that is used by the oil inside the gearbox.
- at least one of the gears is at least partially in an air environment, but may be separated from the air by an oil lubricating film due to its lubrication and its rotations.
- the transmission which can also be referred to as a twin transmission, is preferably equipped internally with an air guiding structure through which air can be diverted from the interior of the transmission to the outside, ie out of the transmission, especially in those cases in which a Air overpressure within the transmission, e.g. B. due to temperature increases, expansion of the lubricant or the inclusion of particles and dirt should occur.
- the vent structure includes a part that can be referred to as a vent channel.
- the venting channel contributes to venting or venting, inter alia, in that air collected in the channel can (indirectly) be passed on to an air exchange point between the interior and exterior of the housing.
- the transition point between what is assigned to the inside of the gearbox, in particular the twin gearbox, and what is assigned to the outside, can be referred to as the actual vent. This venting takes place to vent air, in particular pressurized air or air at a different pressure level than beyond that point of venting.
- venting channel is advantageously guided along a region of the transmission which can also be referred to as a stationary region in the transmission which is otherwise intended for rotating movements (its components such as gear wheels).
- the ventilation duct runs in a stationary axis of the transmission.
- the stationary axis within the gearbox is used to vent the air from inside the gearbox.
- Such a stationary axis can extend from one partial transmission to the other partial transmission. If individual gear wheels of the transmission or shafts are arranged on the axis, or if a stationary axis is selected across such shafts, then one can speak of a stationary cylindrical area in the transmission. Such a cylindrical area can be a gear axle.
- the gear axis is then referred to as the axis at rest.
- the transmission can release air to the outside via the axis at rest.
- the interior of the gearbox can also be supplied with air from outside via the stationary axis.
- a possible, advantageous arrangement results from the selection of an axis through the gearbox in such a way that this axis can also be viewed as a “threading axis” for individual gears of the gearbox.
- the axis through which the air is vented is at the same time a threading axis for gears.
- venting by means of a venting channel for discharging, in particular pressurized, air from the housing of the transmission can be done with the aid of a multi-part venting.
- the ventilation takes place by using the ventilation channel and preferably a multi-part ventilation.
- the housing when it is installed in the direction of travel, is longer than it is wide in relation to the direction of travel.
- the width, i.e. H. the extension running transversely to the direction of travel is usually less than the length in the direction of travel. Individual widths of the housing can be determined in this transverse direction.
- a sleeve-like, elongated, cylindrical, round metal shape which can be referred to as a stationary sleeve, at at least one point within the transmission.
- the ventilation channel can be created in a favorable embodiment by such a stationary sleeve. It is advantageous if the sleeve extends over most of one of several shorter widths of the housing. A central area of the housing in which such a ventilation duct is placed can be selected as a suitable location.
- the ventilation duct can discharge air from other cavities present in the interior of the housing. Air can also get into the ventilation duct via cross bores and escape or spread in the opposite direction of flow in the transmission. Cross bores preferably fulfill at least two functions. There are thus further cavities inside the housing.
- the air is discharged from the interior of the transmission, preferably within the framework of or due to pressure equalization. This allows air to be released to the outside via such a vent.
- the ventilation channel is advantageously within a stationary component, such as. B. a stationary sleeve realized. In the case of a stationary sleeve, this extends inside the housing.
- the resting sleeve has a certain length. In one embodiment, this length corresponds (essentially) to a width of the housing.
- the sleeve extends from the inside of one half-shell of the housing to the other inside of the half-shell of the Housing. The sleeve is thus designed to cover such a width almost completely. In a further embodiment, this length corresponds (essentially) to half the width of the housing.
- the length of the ventilation duct or a component, such as a sleeve, which forms the ventilation duct can amount to approximately up to 25% less than the full or half the width of the housing.
- the sleeve begins at a central area of the transmission and extends to an inner side of the housing.
- the middle area can, for example, be a support point for a rotary bearing or roller bearing that is non-rotatable with respect to the housing.
- the component which comprises the ventilation duct preferably forms a strut from the interior of the housing or through the interior of the housing to the housing wall.
- the component for ventilation e.g. B. the sleeve
- the ventilation channel in particular a flow area of the channel, can open into the interior of the transmission.
- the ventilation channel advantageously has transverse bores. Air can be taken in through these cross bores.
- the in the interior of the component, for. B. in the interior of the sleeve, entering air is then to the outside, i. H. released outside the gearbox housing.
- the ventilation duct can advantageously be created by a separate component, e.g. B. by a hollow, elongated, cylindrical shape inside, which can also be referred to as a "sleeve".
- the inner hollow shape of the sleeve can be a bore.
- the component, for. B. the sleeve provided with a number of, ideally evenly spaced, preferably aligned with a radial component in the sleeve, bores.
- the component creates the actual ventilation channel.
- the component also serves to stabilize the elongated cavity in the interior of the gear unit provided for ventilation.
- the component can have a plurality of ventilation channels, such as a branched ventilation channel system, which is preferably continued by channels which are located in the interior of the housing wall.
- a channel in the housing wall can open into an area of the housing interior without an oil level or into an oil collection chamber.
- the ventilation duct described above can also be referred to as an air receiving space.
- the space which can in particular be designed to be cylindrical, should as far as possible encompass the entire housing, in particular composed of partial housings, at least once.
- a transmission or transmission housing can be produced in that the space extends from a first inside of the housing to a second inside opposite thereto. The space thus penetrates the interior of the transmission. The housing is penetrated by the cylindrical space.
- a suitably long sleeve is suitable as a component for creating an elongated, in particular cylindrical, space.
- the length of the air receiving space is only half as long as a width of the housing in that axis of the ventilation duct.
- a ventilation duct advantageously starts on a central axis of the transmission. From the starting point away, the ventilation channel can run transversely to the axis.
- the sleeve can be perforated by holes that go in particular in different directions.
- a central recess such as a central bore. If the recess, the cylindrical space, is produced by means of a bore, it is advantageous, particularly in terms of production technology, if the bore has been produced with a constant cross section.
- a cylindrically hollow shape of the component that is connected to bores in the housing wall is particularly favorable in terms of a multiple function of the component.
- Oil can get into the cylindrical cavity, which preferably forms a first segment of the ventilation channel, through the bores in the housing wall, among other things.
- Needle bearings in particular which run around the cylindrical metal mold or sleeve as step wheel bearings, can be oiled through transverse bores.
- the cylindrical cavity can serve as an oil reservoir from which oil reaches the needle roller bearings, preferably through oiling openings which conically converge in the radial direction and which open in particular next to a running surface of the needle roller bearings.
- Another segment of the ventilation duct can be a side wall duct which extends parallel to the cylindrical cavity and at a passage opening flows into this.
- the side wall channel has z. B. a diameter of 3 mm to 7 mm, is therefore smaller than a diameter of the cylindrical cavity of z. B. 18 mm to 30 mm. If a flow resistance or a flow barrier for oil, such as an opening, in particular with a flap or a separating body, is present in the ventilation duct or at one end of a narrow area of the ventilation duct, oil can be separated even better from the air flowing out. Oil is held back with the help of an angled configuration of an area of the ventilation duct inside the transmission. A step-by-step reduction in a flow cross-section of the ventilation duct from the inside of the gear unit to the outside is also advantageous for the oil retention.
- a flow resistance or a flow barrier for oil such as an opening, in particular with a flap or a separating body
- the sleeve in particular the exterior of the sleeve, can advantageously be used as a bearing surface, i.e. H. can be used as a bearing for a loose wheel.
- the sleeve can be used as a bearing for at least two idler gears of the same type, one idler gear in each sub-transmission.
- the ventilation duct runs inside the component providing the ventilation duct, and at the same time the exterior of the component is used as a bearing for idler gears that are rotatably seated on this bearing.
- idler pairs which are formed in particular from a larger gear and a gear smaller for this purpose, can be jointly mounted on a section of the ventilation duct or the sleeve.
- a continuously variable wheel can be formed as a welded assembly from two idler wheels that are non-rotatably connected to one another. The diameters of idler gears designed in this way are different. The larger gear has a larger diameter than the smaller gear.
- the gears which can be described as large gear and small gear, become a synchronously rotating, e.g. B. manufactured by joining together tied total gear (in the sense of a stepped gear), the exterior of the ventilation duct is used for the stepped gear storage.
- the assembly to which z. B. may include a sleeve, and gear pairs mounted thereon can thus be used for a freely rotating spur gear transmission stage.
- Each spur gear ratio stage belongs in its own sub-transmission.
- the respective spur gear ratio stage can be a stage of an at least two-stage reduction gear.
- the step gear is arranged in particular as an intermediary gear between the first stage and the second stage. It can also be from a second, e.g. B. middle, translation assembly are spoken, which includes the step gear.
- the step gear is in mesh with a first gear, an input gear and a second gear, an output gear, whereby one transmission stage in each case is trained.
- the stepped gear or the transmission assembly of the stepped gear occupies a space of the interior of the gearbox housing.
- the space area can at least partially comprise a ventilation duct.
- the step wheel can preferably be rotated around a region of a ventilation duct into which, in particular, lubricating oil can also enter or emerge from the lubricating oil.
- the ventilation channel can be passed between two bearings.
- the bearings are implemented by roller or plain bearings, e.g. B. with bearing rings, the bearings have an orientation that results, for example, from a cut in the transverse direction to the shaft to be supported.
- the z. B. ring-like bearings can be cut like a secant through their rings at one point, which corresponds to an orientation of the bearing.
- a connecting line between the individual components of the ventilation can be present so that the ventilation is brought to the ventilation duct.
- a component can e.g. B. be a vent line.
- the vent line connects the air, preferably coming from the vent channel, to the vent.
- the ventilation is therefore advantageously implemented in several parts or in several components.
- the exterior of the vent duct, its z. B. sleeve can be equipped with a further tubular, in particular elongated, (elongated) hole, which, for. B.
- the ventilation feed line at right angles to the actual ventilation duct or parallel to the actual ventilation duct, represents a ventilation feed line in an edge area.
- the ventilation feed line can be made shorter than the actual ventilation duct.
- the venting feed line is a venting channel preliminary stage which is reduced in diameter and in particular slows down and reduces internal flows in the housing.
- the ventilation in the transition area to the outside ie where the ventilation channel continues to the outside, can be covered by a ventilation cap.
- a venting of the tube can be realized, with z. B.
- the breather cap comprises a single needle seat.
- the needle seat can serve as a needle bearing for a valve needle.
- the breather cap opens due to pressure gradients, e.g. B. because it works as a pressure relief valve or includes a pressure relief valve.
- a pressure relief valve may be a type of pressure relief valve which operates with a flat seat. It is particularly advantageous if the vent cap is equipped to open when there is a pressure difference between inside and outside and without a pressure difference remains closed, so z. B. by the pressure differential providing a valve actuation force.
- the admission of oil to the vent channel can be reduced by choosing a location for the vent and its components within the housing which is arranged above a maximum level of the oil. If the location of the vent is chosen so carefully that even the gearbox tilt angle that is below an upper limit, such as B. 40 °, 45 ° or 50 °, cause only such a small change in the position of the gearbox that the oil in the sump does not get into the ventilation duct, is even on rough terrain, when driving on a bumpy road or when driving inclines Reduced risk of oil entering the ventilation duct.
- the maximum level is not fallen below, even if the transmission in relation to its regular installation position at a larger angle, such as. B. by 40 °, 45 ° or 50 °, is tilted (z. B. due to a hill climb of the vehicle).
- the venting can also be designed in such a way that the venting provides a security against rotation of the gear housing.
- the vent creates an assembly orientation if it is designed in such a way that only a single assembly orientation of the gearbox housing is possible due to the vent.
- This makes it possible to first produce identical gear housing halves, for. B. by die casting, wherein in one of the half-shells, d. H. the ventilation is installed in one of the gear housing parts, whereby the initially identical gear housing half-shells differ from one another. For example, due to the sleeve to be installed, the right gear housing shell differs from the left gear housing shell.
- the entire ventilation section can be divided into individual sections. Even the actual ventilation duct can also be divided into different sections. It has proven to be particularly advantageous if the ventilation channel is a channel structure that is guided in parallel and has different diameters.
- An advantageously central, thicker section is accompanied by a weaker, laterally arranged section. The weaker section lies outside the thicker section and runs parallel to the latter section.
- the ventilation duct can be configured in several parts or composed of several sections.
- two different sections can put together the ventilation duct.
- a first section is made stronger or thicker than a second section. Both sections can run parallel to one another or even arranged in the same way in the sleeve. If the weaker section is connected upstream of the stronger one, the weaker section is used for oil throttling, as a result of which oil mist ingress into the larger ventilation duct can also be held back.
- the individual sections that z. B. take over functions such as collecting the exhaust air, separating oil, retaining oil or making it difficult to guide oil, e.g. B. in the event of the vehicle carrying the transmission tipping over, the individual sections can be connected to one another by transition areas.
- transition areas By means of a folded, nested or multiply deflected channel structure, in particular with the addition of transition areas, i. H. z. B.
- a ventilation structure can be formed in the transmission, which on the one hand Retains transmission oil, but on the other hand provides a reliable, as oil-free venting as possible, although a larger area or a larger section in the form of the ventilation duct is designed in a stationary position in the transmission. Between the individual sections, transition areas can also be provided, which z. B. can establish a single connection between a first section with a certain diameter and a second section with a different diameter.
- a multiple deflection makes it possible to further reduce the oil leak, whether as an aerosol, as a droplet or as a film.
- bearing bracket which can be viewed from one perspective as a separating element of the (partial) gearbox.
- the double transmission has a common bearing bracket. Via its sleeve around its annular inner opening, the bearing bracket supports the respective output shaft reaching in at one end. That is, the two output shafts, which are arranged in particular with a respective end face parallel to each other in the bearing bracket or its opening, with both end faces preferably being spaced from one another, lead out of the bearing bracket into an area outside the housing of the double transmission.
- the bearing bracket is, so to speak, in the middle between two gear housing half-shells.
- the bearing glasses are - under a different perspective - the central, central component that separates the individual gears of the double gear.
- the bearing bracket separates the gear space of the double transmission into a left half (in the direction of travel) and a right half. Via an interface between the two halves of the double transmission, on which the bearing bracket extends, which can be drawn in as a construction aid, transmission oil flows through or is exchanged, but not torque transmission.
- a bearing bracket which can be present as a component of a double transmission in this, can exist around a hole structure.
- the hole structure is in the center of the bearing frame.
- the central hole, the hole structure is for receiving two ends of output shafts, i.e. H. a first end of a first output shaft and a second end of a second output shaft.
- Such a bearing bracket can be installed in a double transmission, as was presented above.
- the output shafts are supported by a single bearing bracket in an end region of the output shafts.
- the bearing glasses whose designation as "glasses" stems from the fact that two output shafts are supported, could also be referred to as a bearing monocoque because the output shafts extend lengthwise together on a line so that their radii overlap when viewed perpendicular to the longitudinal direction of the housing.
- the bearing bracket preferably has a single, in particular central, hole structure.
- the hole structure preferably takes two output shafts at one of their ends.
- the hole structure includes, in particular, two floating bearings.
- a floating bearing can support a wheel half-axis, in particular if a shaft of the wheel half-axis extends into the gearbox housing.
- the bearing bracket is preferably attached to a support structure in the interior of the housing. No sealing surfaces need to be provided between the bearing bracket and the housing. Such sealing surfaces could become leaky due to mechanical loads in continuous operation.
- the transmission can be equipped with a single part housing connection surface.
- each barrel bearing is designed to receive one end of one of the output shafts.
- the respective barrel bearing accommodates an output shaft.
- an axial extent such a barrel bearing can be referred to as an outermost (or, depending on the viewing direction, innermost) bearing for a wheel half-axis or wheel drive shaft.
- a further bearing on the gear housing via a ball bearing such as a deep groove ball bearing.
- a value for the angle ⁇ is selected for the projection which leads to a minimization of the radial force transmission from a first gear to a second gear.
- the first gear can be designed for a clockwise direction of rotation (in the case of a motor drive).
- the second gear is designed for one direction of rotation to the left (in the case of a motor drive).
- the teeth of the gears have tooth flanks (inclinations or angled tooth surfaces). At this angle setting or inclination, a tooth of a first gear wheel drives a tooth of a second gear wheel.
- the transmitted driving forces can be divided into their radial and axial components. While the radial part should be transferred as well as possible, it is desirable if the axial part is compensated as much as possible, e.g. B. is only settled in an order of magnitude of the force that is in the single-digit percentage range compared to the radial portion.
- the angle ⁇ of the projection corresponds to the tooth flank steepness of the teeth of the first and / or the second gear.
- the gear radii of the first and second gearwheels go into the angle ⁇ of the projection. Initially, theoretically, the projection “upwards” and “downwards” can be selected. The “upward” projection has proven to be particularly advantageous (see the explanations given in other places).
- the input shaft (s) and / or the output shaft (s) as also on z. B. to design sleeve-like hollow bodies mounted shafts.
- a cantilever of gear positions or gear positions of a gear or even of several gears, which are assigned to one or more stage (s) of the transmission, is made possible, especially in pulling mode, whereby the electric drive motors can be positioned behind the vehicle axle
- the vent can be composed of a certain number of individual sections, so the vent can comprise only one section, two sections, three sections, four sections or even more than five sections.
- At least one of the sections can be used to transfer transmission fluid such as oil that reaches that section, also via bearings, e.g. B. by way of their lubrication to divert. So it is possible to use oil to lubricate the bearings of gears that rotate around the axis used as a ventilation structure.
- the presented vent can be easily produced and is still a reliable vent for transmission, because z. B. has been selected as a position a resting center in the center of rotation of gears of a gear stage.
- venting presented here can be used particularly advantageously in twin transmissions, which are preferably equipped with a total oil chamber, but can actually be viewed as two independent transmissions.
- Figure 1 shows a vehicle system in principle
- Figure 2 shows another example of a vehicle system in a schematic diagram
- FIG. 3 shows a transmission shown in principle in a longitudinal section
- FIG. 4 shows a transmission shown in a schematic representation in a side, open view
- FIG. 5 shows a transmission shown in a schematic representation according to FIG. 4 in a rotational state
- FIG. 6 shows a schematic diagram of a further example of a transmission in a longitudinal section
- FIG. 7 shows a drawn-out section from the transmission from FIG. 6 with an alternative embodiment of a stiffening pipe used for ventilation
- Figure 8 shows a variant of an advantageous transmission with a vent in a schematic diagram
- Figure 9 shows a development of a double input shaft for a transmission with which a transmission likes.
- Figure 6 can advantageously be further developed.
- FIG. 1 and Figure 2 each show a schematic representation of a motor vehicle 500 and 500 ', which in addition to the space for the driver, recognizable by the steering wheel 514, which can also be referred to as a driver's cab or passenger cell, has a rear 526 and a trunk area 528 , recognizable by the direction of travel 502.
- the steering wheel 514 which consists of a steering shaft, steering gear, tie rods and steering levers via a steering linkage 516, on two wheels as road wheels 510, 512 steering movements one Driver can transfer.
- Two further road wheels 506, 508 are attached to a second axle, the vehicle rear axle 518.
- a wheel or road bike can also be referred to as a vehicle wheel because it is the
- Movement of the motor vehicle 500 or 500 ' is used.
- the road wheels 506, 508 are driven via semi-axles 520, 522, the drive shafts.
- the semi-axles 520, 522 are attached to a double gear 1 or 1 IN on the output side.
- On the drive side of the double transmission 1 or 1 m are a first electric machine 5 or 5 ′′ and a second
- Electric machine 7 or 7 M attached.
- Semi-axles 520, 522 are each attached in pairs on opposite sides of the gear 1 and 1 IM . Torque from the electric machine 5 or 5 ′′ is applied over one side to an input shaft 33 (cf. FIG. 3) of the double gear 1 or 1 m and the first semi-axis 520 is attached to the same side of the double gear 1 or 1 IM , thus the output on the first road wheel 506. In the same way, from the electric machine 7 or 7 ′′ to an input shaft 35 (see FIG. 3) of the
- Double gear 1 or 1 IM torque is applied and the second half-axis 522 is arranged on the same side of the double gear 1 or 1 m , thus the output on the second road wheel 508.
- a particularly advantageous motor vehicle structure is when the electric machines 5, 7, which are mounted in front of the semi-axles 520, 522 in the direction of travel 502 according to FIG. 1, are mounted behind the semi-axles 520, 522, as shown with reference to the electric machines 5 ", 7" in FIG are e.g. B. in that the symmetrically constructed double transmission 1 is rotated 180 ° in the plane of the vehicle floor 504 shown in FIG. 1 and, in particular, assembly points for the double transmission 1 or the electrical machines 5, 7 are present under the trunk 528.
- a drive train 3 'with a double transmission 1 IM can also be built up in a motor vehicle 500', the gears of which (see FIG. 3) are used for power transmission in an arrangement of the electric machines 5 ", 7" are designed behind a rear axle 518 1 .
- an electrical accumulator 9 which supplies electrical energy to the electrical machines 5, 7 or 5 ", 7" and their (not shown) motor controls via electrical lines 1 1, 13 Can provide.
- the drive train 3 or 3 'thus extends from the accumulator 9 over the electrical lines 11, 13, over the electric machines 5, 7 or 5 ", 7” and their motor controls, over the double transmission 1 or 1 IM and over the semi-axles 520, 522 to the road wheels 506, 508.
- an electric machine 5, 7 or 5 ", 7” drives a road wheel 506, 508. It is a single wheel drive.
- the transmission 1 or 1 IM is arranged on the vehicle longitudinal axis 524.
- An electric machine 5 or 5 ′′ and a semiaxis 520 are located on one side of the vehicle longitudinal axis 524, the other electric machine 7 and the other semiaxis 522 are arranged on the same side on the other side of the longitudinal axis 524.
- the rotating transverse to the vehicle longitudinal axis 524 according to FIG , centrally arranged electric machine 5 or 7 rotates the transmission 1 so that on the output side, also transversely to the vehicle longitudinal axis 524, an output shaft 37, 39 (see FIG. 3) can apply a torque to a wheel 506 or 508.
- FIG. 3 The according to FIG.
- the vehicle 500 or 500 ′ shown in FIG. 1 and FIG. 2 is driven via its vehicle rear axle 518 or 518 1 . It is an electric rear axle drive with the help of the double gearbox 1 or 1 m .
- the double transmission 1 or 1 IM is arranged in the area of the rear 526 or in the area of the trunk 528 and there in the area of the vehicle floor 504. It is particularly favorable if FIGS. 3 and 4 are considered together.
- the transmission 1 is shown in FIG. 3 in a sectional view and the transmission 1 1 is shown in a sectional view in FIG. 6, in which the section is guided through the individual gear centers 25, 27, 29.
- the gear 1 m of Figure 2 can be designed like a gear 1 according to Figure 3 or like a gear 1 1 according to Figure 6 or like a gear 1 ′′ according to Figure 8, the gear housing each having fastening points for mounting near the trunk (not shown) .
- each spur gear has three positions 19, 21, 23 for gear centers 25, 27, 29 in a single, common gear housing 31.
- the drive torque 5 ′, 7 ′ is applied to the respective input shaft 33, 35 by the electric machines 5, 7 (see FIG. 1).
- the input shafts 33, 35 connected to the respective electrical machines 5 and 7 (see FIG. 1) and the output shafts 37 and 39 connected to the respective semi-axes 520 and 522 are in a central region M, based on a transverse extension, ie in particular a shorter distance from a housing wall 41 to a housing wall 43 of the transmission housing 31 opposite it, lying at the same height.
- the position of the input shafts 33, 35 and the output shafts 37, 39, which define the gear centers 25 and 29, describes a reference plane B within the gear housing 31.
- a central axis 45 which has a central gear center 27 or the central position of an axially mounted gear 49, 49 ′, 50, 50 ′, is angled or raised to the reference plane B and forms a position of the gear wheel center 27 remote from the transmission housing bottom.
- the two input shafts 33, 35 are joined together to form a double input shaft 32. They are mechanically connected to the double input shaft 32.
- the two input shafts 33, 35 extend along the axis 44 and in this way form the double input shaft 32.
- the two input shafts 33, 35 arranged coaxially are connected to one another so that they can rotate relative to one another.
- the central axis 45 lies in a corner of a triangle 47 spanned by the gear centers 25, 27 and 29.
- the central axis 45 can be cut via a straight line g connecting the gear wheel center 25 or 29 and the central axis 45, specifically in an angular range of approximately 5 ° to 70 °.
- each individual gear 15, 17 drives a respective gear 49, 49' on the central axis 45, the directions of rotation of the electric machines 5, 7 (see FIG. 1) in the pulling mode of the Vehicle are selected so that the gear 49, 49 'has a sense of rotation turning away from the housing bottom 51 of the gear housing 31 after a gear wheel contact in a driving manner.
- the arrow indicating the direction of rotation in FIG. 5 illustrates this definition of the directions and the sense of rotation.
- the double transmission can also be operated in the reverse direction of the arrows for the direction of rotation, in particular for reversing.
- the axis 45 defining the middle position or the middle gear wheel center 27 is designed as a stationary axis fixed to the housing. This enables the gear housing 31 to be stiffened without the need for additional components.
- the respective driven gear 49, 49 'on the axle 45 and the driving gear 50, 50' are mounted on the axle 45 via two needle bearings 61, 63, 61 ', 63' in order to prevent the gears 49, 50 and 49 from tilting ', 50' which, moreover, are preferably formed in pairs as a one-piece step wheel.
- the input shafts 33, 35 and the output shafts 37, 39 are supported by roller bearings 65, 67, 69 and 71 in the outer walls of the gear housing 31. Furthermore, the input shafts 33, 35 are mounted in the vicinity of an intermediate housing wall 73, which has openings for common lubrication of the individual gears 15 and 17, by means of ball bearings or a separate ball bearing for each individual gears 15, 17.
- the output shafts 37 and 39 are mounted in a second intermediate housing wall 73 ', more precisely a bearing bracket, by means of needle bearings (without reference symbols) or one needle bearing for each individual gear 15, 17.
- the input shafts 33, 35 and the output shafts 37, 39 are arranged lower than the axis 45 in relation to the housing bottom 51 of the gear housing 31.
- the step gears 79, 79 '(see Figure 6) on the axle 45 have a first, larger diameter d 2 on the drive side and a smaller, second diameter d 3 on the output side (see Figure 3). There is a reduction to the output side. It can also be said that the two gears 49, 50 or 49 ', 50' are joined or welded together to form a step gear 79 or 79 '.
- FIG. 3 or FIG. 6 and FIG. 4 or FIG. 5 are considered at the same time, the result is that the larger diameter d 2 is towards the interior, the smaller diameter d 3 is closer to the housing 31 (in comparison to this). So it is possible that in the transmission 1 initiated moments in the direction of the output shaft 37, 39 to the outside. Due to the planes of the transmission 1 in which the gear centers 25, 27, 29 are located, and due to the arrangement of the steps 53, 55, the torque profile follows a double V-profile (once in relation to heights to a floor, in particular the Housing bottom 51 of the transmission 1, once in relation to a divergence away from a vehicle longitudinal axis 524 (see FIG. 1)).
- the gear wheel 75 of the input shaft 35 according to FIG. 5 has a first direction of rotation 85 directed towards the housing base 51.
- the larger gear wheel 49 of the step gear 79 which is driven via the input shaft 35, has a second direction of rotation 87, which is directed away from the housing base 51 on the drive side.
- the output gear 77 which meshes with the smaller gear 50 of the stepped gear 79 and is driven by this in a third direction of rotation 89 towards the housing bottom 51, is rotated around the third gear center 29.
- the transmission 1, as shown in FIG. 5, is particularly compact and space-efficient.
- the housing 31 is shown schematically in FIG. 5 in an open state using the first partial housing 95.
- the first partial housing 95 can be connected to a shell-like second partial housing (not shown) on a flat sealing surface 91.
- the connection of the similarly curved partial housings, such as the partial housing 95, is carried out with the aid of bolts which can be screwed into the bolt thread 93 of the first partial housing 95.
- the sealing surface 91 extends parallel to the triangular surface spanned by the positions 19, 21, 23. In other words, the sealing surface lies in a plane parallel to the gears 75, 77, 79. It can also be said that the input shaft 35 is arranged at right angles to the sealing surface 91 or at right angles to the partial housing connection surface 91 in the gear housing 31. This facilitates the assembly of the transmission 31.
- the housing longitudinal direction 190 shown in Figure 6 is aligned parallel to the vehicle longitudinal axis (see vehicle longitudinal axis 524 in Figure 1 and Figure 2).
- the transmission housing 31 has a greater extent in its longitudinal direction 190 than in its width 106.
- there is a first gear stage 53 or first gear ratio 53 which forms a gear ratio that turns away from the housing bottom 51 of the gear housing 31, and a second gear stage 55 or the second gear ratio 55, which forms one on the housing bottom 51 appropriate translation forms.
- the gear pairing of the first two gear wheels 75 ', 49' creates the translation 53 'in the torque flow of the transmission 1.
- the gear pairing of the two subsequent gears 50 ', 77' creates the translation 55 '.
- the central, integrally formed gear wheels 49, 50 and 49 1 , 50 1 are designed for a transverse force-free transmission of a torque by the teeth 57 and 59 or 57 1 and 59 1 of two adjacent gears 49, 50 or 49 1 , 50 1 have different helix angles for each row of teeth, such as helix angles ßi and ß 2 .
- the helix angles ß ⁇ ß 2 are - to promote understanding - only indicated schematically in the sectional plane shown in Figure 3 and Figure 6.
- the teeth 57, 59 of the partial transmission 17 and adjacent teeth of the respective rows of teeth extend with respective tooth directions parallel through the sectional plane of FIG. 3 and FIG. 6.
- the teeth 57, 59 or their running surfaces extend with respect to a predetermined or selected direction of the central axis 45 with one tooth direction similarly laterally to the other partial transmission 15 or away from the other partial transmission 15, with a deviation of the tooth directions expressible by vectors of the teeth 57, 59 from the direction of the central axis 45 each have the same sign for their vector values (identical sign in the helix angles).
- the gears 49, 50 or 49 ', 50' are free of axial forces, at least when the vehicle is in pulling mode.
- the gearwheels 49 ', 50' or the teeth 57 ', 59' of the other individual gear 15 the same applies due to a similar structure of gear parts, i.e. That is, the partial transmission 15, which is constructed in the same way as the partial transmission 17, has adjacent gears 49 ', 50', which are correspondingly designed with an inclined position of the teeth 57 ', 59'. I.e. for the gearwheels 49 ', 50' or the teeth 57 ', 59' of the other individual gear 15, because of a similar structure of gear parts, the previously described applies in a corresponding manner.
- the gears 49, 49 ', 50, 50', 75, 75 ', 77 and 77' are formed as disk wheels because of the high torques to be transmitted.
- the output shaft-side gears 77 are formed with a washer which is less thick than the width of its ring gear.
- the respective disk of the gear wheels 77, 77 ' is angled to the respective output shaft 37, 39. That is to say, it can be formed at an angle to the respective output shaft 37, 39 that is different from the perpendicular angle.
- the disk has a base with an end face which extends radially from the output shaft 37, 39 or merges into the output shaft 37, 39 and in particular delimits a running surface of a needle bearing in an axial direction.
- All gears, axles and shafts installed in the gear housing 31 are lubricated via a common sump.
- Each individual gear 15, 17 has a speed ratio of, for example, 8.5: 1 or even 12: 1.
- the positions 19, 21, 23 of the gear centers 25, 27, 29 are located in a central region M within the housing walls 41, 43.
- the toothed wheel 49 with its teeth, such as the tooth 57, and the toothed wheel 50 with its teeth, such as the tooth 59, is, as a stepped gear, the gear which is arranged furthest upwards from the housing base 51.
- a stepped gear as it is formed from the gearwheels 49, 50, is driven in pulling mode by an input shaft 35, which is part of the double input shaft 32 (see FIG. 3).
- each gear 75, 75 ′ is designed as a ring gear 58 that is integral with the double input shaft 32.
- the ring gear 58 is part of the input shaft 35.
- the input shafts 33, 35 are separated from one another by an air gap 83 in the area of their gears 75, 75 '.
- Ball bearings 81, 81 ' via which the double input shaft 32 is supported with respect to the housing 31, in particular via the bearing-bearing intermediate housing wall 73, are arranged adjacent to the gears 75, 75'.
- Each partial transmission 15, 17 runs, as shown in particular in FIG. 5, in its own Part of the transmission space 97, which is formed at least in part by the transmission pan or housing pan 95.
- the transmission housing 31 In a regular state of filling with a transmission oil, the transmission housing 31 is not completely filled with oil, but rather a part of the interior space, ie. H. of the inner volume 108 (see FIG. 6) of the gear housing 31 is filled with air.
- the transmission 1 1 shown in FIG. 6 with its transmission housing 31 creates an inner volume 108 extending from its first inner side 102 to its second inner side 104 through its inner cavity.
- volume-reducing components are arranged in the inner volume 108.
- the inner volume 108 is created by the gears, such as the gears 49, 49 ', 50, 50', 75, 75 ', 77, 77', by shafts, such as the shafts 33, 35, 37, 39, and by other components, like needle roller bearings 61, 61 ', 63, 63' and roller bearings, and partly reduced by a sleeve 116.
- the free internal volume 108 is reduced by the built-in components.
- the remaining interior volume 108 is filled for the operation of the transmission 1 1 with a transmission fluid such as a gear oil, up to a certain level. Air remains in the remainder of the inner volume 108.
- a venting structure is incorporated in the transmission 1.
- the sleeve 116 which is hollow through a bore 118.
- the cavity created by the bore 118 in the interior of the sleeve 116 has via further bores 118 1, 118 "connections to the rest of the internal volume 108 of the transmission 1 1 and the transmission housing 31.
- the additional holes 118 ', 118" extending transversely, in particular orthogonally to the one bore 118th
- the sleeve 116 extends from one inner side 102 to the opposite inner side 104 of the gear housing 31.
- the sleeve 116 is a cross brace that stiffens the housing 31.
- An (inner) width 106 of the gear housing 31 is completely spanned by the sleeve 116.
- the sleeve 116 therefore extends from a first housing wall 41 to a second housing wall 43.
- the sleeve is located in the transmission 1 1 a central area M 116th
- the middle area M of the transmission 1 1 is used by the second, middle position 21 for the centering of gears 49, 49 ', 50, 50'.
- Air from the inner volume 108 can via the (supply) bores 118 1 , 118 ′′ into the centrally arranged bore, in particular spanning the width 106 of the housing 31 118 of the sleeve 116. The air then reaches the breather cap 130.
- housing wall 41, 43 there can be further bores (not shown) extending in areas along the housing wall 41, 43, through which the air can enter the width 106 of the Housing 31 spanning bore 118.
- Such housing wall bores also serve to supply oil to the needle bearings of the gear wheels 49, 49 ', 50, 50'.
- a thinner portion 136 is connected to the thicker section 134 outside a center 110 of the transmission 1. 1
- the thinner portion 136 of the vent extends less than half the distance of the sleeve 116.
- FIG. 7 shows a section from a sleeve 116 1 , which is designed as an alternative to the sleeve 116 in FIG. 6, together with a section from the housing wall 43 and the gears 49, 49 1 , 50, 75, 77, which are also shown in FIG , in an enlarged view.
- the needle bearings 61, 63 can also be seen under the gears 49, 50.
- the sleeve 116 1 shown in FIG. 7 offers more functions than the sleeve 116 according to FIG. 6. However, the dimensions of the sleeves 116, 116 1 are the same.
- the ventilation according to FIG. 7 offers a ventilation cap 130 which is connected to the ventilation tube 132, which is attached to a trunk 131.
- the trunk 131 is connected to the ventilation tube 132 as an extension that widens the flow cross-section.
- a trunk length of a trunk of a trunk curvature or exit angle can be set a Entlmultiungsort, especially in a distance to a surface of the transmission (see FIG. 1 gearbox 1 in Figure 6).
- Several sections 134, 136 are assigned to the ventilation duct 124.
- the sections 134, 136 can also be referred to as ventilation channel segments.
- the venting channel 124 is divided into several sections 134, 136, some of which run parallel to one another and some of which run at right angles to another section.
- the sections 134, 136 are equipped with different diameters. In this way, influence on the flow behavior of the air in a transmission such as the transmission 1 1 (see FIG. 6) are created.
- the ventilation channel 124 has a section 134 which, due to its larger diameter 126 than the actual one in comparison with the other sections, such as the section 136 Ventilation channel 124 applies.
- the enlarged section of one end of the sleeve 116 1 shown in FIG. 7 shows the vent structure inserted into the housing wall 43, to which the vent tube 132 with the vent cap 130 and the multiple angled channel guide with its sections 134, 136 and its transition areas, such as the transition area 138 , belong.
- the thickest section 134 is the ventilation channel 124 with the largest cross section 126. Bores 118 1 , 118 '"and oiling passages, such as the oiling passage 152, extend from the ventilation channel 124.
- the ventilation channel 124 is advantageously itself a bore 118 Bore 118 is spoken of when it refers to elongated channels with a uniform cross section 126, in particular extending over the width 106 of the housing (see FIG.
- the sleeve 116 1 in its middle That is, a space 122 in which an air-oil mixture, for example as an aerosol, can be present.
- an air-oil mixture for example as an aerosol
- Such bearings 63 may be designed as a needle bearing 61.
- the sleeve 116 1 d ient therefore not only to provide space 122 for ventilation, but also as a bearing 144, 146 for idler gears, such as idler gear 148.
- Rotating around sleeve 116, gears 49, 49 ', 50, which are in engagement with further gears, in particular the gears 75, 77 are, form spur gear ratio stages, such as the spur gear ratio stage 150.
- the sleeve 116 1 is a bearing for other gears, such as the gear 49 1 .
- An oil-air mist can enter the channel 124, which belongs to the ventilation structure, via transverse bores, such as the transverse bore 118 1 .
- the oiling passages, such as the oiling passage 152, are arranged in the sleeve 116 1 in order to direct oil back to the bearings 144, 146.
- Air from the air-oil mixture can flow via the vent line 128 to the vent cap 130 in order to avoid excess pressure, e.g. B. based on an environmental environmental pressure, to the environment from the transmission, such. B. the transmission 1 1 of Figure 6 to be delivered.
- the transmission 1 M according to Figure 8 has a center 110 '.
- the bearing bracket 73 ′′ is arranged in the housing 31 ′ with its central hole structure 154 in a region of the center 110 ′ of the gear 1 ′′ or of the housing 31 ′.
- a sleeve 116 "leads from the bearing 146 1 of the output gear 77 ′′ along a stationary axis 112, which is provided with a bore 118 IV , whereby air can be discharged via the venting element 130 1 .
- the bore 118 IV in the sleeve 116 ′′ represents the connecting channel or ventilation channel 124 1 from the center 110 1 or from an inner region of one of the central hole structure 154 of the bearing bracket 73 ′′ to the ventilation element 130 1 .
- the bearing bracket 73 ′′ has a single hole structure, namely the central hole structure 154, which is used to accommodate two bearings 144 1 , 146 1. Of these two bearings 144 1 , 146 1 , only the one behind the vent channel 124 1 disposed bearing 146 1 is shown. the other bearing 144 1, indicated by dashed lines, sitting congruently before the drawn stock 146 1. in other words, the venting channel opens into an air space 156 between two bearings 144 1, 146 1. the airspace 156 is annularly surrounded by the bearing bracket 73 ′′. The air space 156 is part of the inner volume 108 1 or belongs to the inner volume 108 1 .
- a bearing bracket attachment 158 is surrounded by the inner volume 108 1 of the housing 31 ', which can also be referred to as the gear housing 31'.
- the bearing bracket attachment 158 is designed as a four-point attachment. In other embodiments, two-point fastenings or three-point fastenings or other anti-twist fastenings can be used.
- the bearing frame attachment 158 has two bearing frame bifurcations, such as the bearing frame bifurcation 159, which in each case divert tangential forces or transverse forces, which can act on the bearings 144 1 , 146 1 , into the gear housing 31 1 like a lever arm.
- the bearing bracket is connected via the bearing bracket attachment 158 to a bearing bracket support structure 155 inside the housing 31 '.
- the two sub-housings of the housing 31 ′, for. B. be joined together in a fluid-tight manner by inserting a seal or a sealant (not shown).
- the transmission 1 M has several spur gear ratios 150 1 , 150 ′′.
- the gear 1 M has a step gear 79 '.
- the spur gear ratios 150 1 , 150 "are very different stored, e.g. B. by a bearing bracket 73 ′′.
- the transmission 1 M offers several centers 1 10 1 , 110 ′′, which can advantageously be used for ventilation via ventilation channels 124, 124 1 .
- the channels 124, 124 1 are in sleeves, such as. B. the sleeve 1 16 "out.
- the sleeve 1 16 "runs along the axis 1 12, which is arranged transversely to the axis of rotation of the gear 77".
- the gear 77 ′′ is rotatably mounted on the bearing bracket 73 ′′ via a bearing 146 1 .
- a venting channel 124 1 is led up to the gear housing 31 ', more precisely out of the gear housing 31', by means of a transverse bore 142 in the bearing bracket 73 ".
- the gear housing 31 ' has a width 106 1. Because the ventilation channel 124 1 starts only from the area of the bearings 144 1 , 146 1 and extends to the housing 31 1 , the ventilation channel 124 1 is (only approximately) half as long as the width 106 1 of the gear 1 M.
- the ventilation channel 124 1 extends along the axis 112 running transversely to the axis of rotation.
- the ventilation channel 124 1 opens into the ventilation element 130 1 .
- the vent element 130 1 is located outside the gear housing 31 '.
- the ventilation channel 124 1 has been formed in the sleeve 116 ′′ by a bore 118 IV , which runs transversely to the axis of rotation.
- the sleeve (without reference number) for venting arranged between the spur gear ratios 150 1 , 150 ′′ has an elongated vent hole produced by a bore (without reference number).
- the bore runs inside the sleeve (see sleeve 116, bore 118 in FIG. 6).
- FIG. 9 shows a further development of a double input shaft 32 1 , which is advantageous for a double transmission.
- the double input shaft 32 1 has two gears 75 ′′, 75 m , each of which is formed as a ring gear 58 1 or 58 ′′ between two ball bearings 177, 179. Both gears 75 ′′, 75 m are between the ball bearings 177, 179.
- the double input shaft 32 ' has two drive couplings 1 17, 1 19.
- Each Drive enclosure 117, 119 is provided on a stub 165, 167 of the double input shaft 32 'formed by stub shafts 161, 163.
- a drive enclosure 117, 119 is used to be surrounded by a connection (not shown) in a torque-locking manner.
- the drive enclosure 117, 119 comprises a splined shaft profile 105, 107 in a shaft jacket 109, 111.
- the shaft jacket 109, 111 begins at the end of a shaft end 113, 115.
- the stub shaft 161, 163 offers through the splined shaft profile 105, 107 in the shaft jacket 109, 111 a good positive and / or non-positive connection to the electric machine 5, 7 or 5 ", 7" (see Figure 1 and Figure 2).
- the two stub shafts 161, 163, which together are essential parts of the double input shaft 32 ', are designed as stepped shafts 169, 171.
- the largest step in the stepped shaft 169, 171 is the step of the integrated gear rim 58 'or 58 ".
- the gear rim 58', 58" is designed as a gear 75 ", 75 m with a gear wheel 101, 103.
- Each gear wheel 101, 103 belongs to its own gear 75 ", 75 m .
- the air gap 83' allows the gearwheels 101, 103 to rotate almost smoothly next to one another, in particular at different speeds.
- the stepped shafts 169, 171 each have their own pair of bearings 173, 175 for support against the only indicated housing 31 '.
- Each pair of bearings 173, 175 is composed of a deep groove ball bearing 177, 179 and a cylindrical roller bearing 181, 183.
- the two step shafts 169, 171 are rotatably engaged with one another on the axis 44 via two shaft bearings 145, 147.
- Advantageous examples of shaft bearings 145, 147 which are only shown in very abstract form, are plain bearings or needle bearings.
- the shaft bearings 145, 147 have different diameters.
- the shaft bearings 145, 147 are grooved on the first, internal stepped shaft 169, in particular its journal area 162, and are supported on the second stepped shaft 171 coaxially surrounding the first stepped shaft 169 in its journal area 162, in particular in its journal receiving area 164. Between the journal area 162 and the journal receiving area 164, in addition to the shaft bearings 145, 147 and between the shaft bearings 145, 147, there is an air gap 83 ′′.
- the stepped shaft 169 can be viewed as a two-way stepped shaft with the largest diameter and the gear 75 ′′.
- the second step shaft 171, starting from the largest diameter below or next to the gear 75, is a step-wise tapering shaft that enters the spline profile 107 as the smallest diameter the stepped shaft 171 runs out.
- the second step shaft 171 is a partially hollow shaft.
- the first step wave 169 is a solid wave throughout.
- the stepped shaft 171 is also a massive stepped shaft. Only in the area of the shaft bearings 145, 147 or in the ring gear 58 'with the gear 75 is the stepped shaft 171 gradually hollow.
- the other stepped shaft 169 is received with its pin area 162 in the cavity, the pin area extending away from the gear 75 ′′ and under the gear 75 of the partially hollow step shaft 171.
- the narrower shaft bearing 147 which can also be said to have a smaller diameter, is located inside the pair of bearings 175.
- the smaller shaft bearing 147 is flush between the bearings 179, 183 of the second pair of bearings 175.
- Below the gear wheel 75 m is the other Shaft bearing 145.
- the second shaft bearing 147 lies opposite the bearing pair 175 in a plane perpendicular to the axis of the input shafts 44.
- the first shaft bearing 145 is assigned to the gearwheels 101, 103.
- the two step shafts 169, 171 are connected to one another via shaft bearings 145, 147.
- Each stepped shaft 169, 171 is supported against a housing part by a combination of deep groove ball bearings 177, 179 and cylindrical roller bearings 181, 183.
- Plain bearings and needle bearings are particularly preferred as suitable shaft bearings 145, 147.
- a plain bearing or a needle bearing is installed either at one point or another.
- stepped shafts 169, 171 are designed as stub shafts 161, 163. It is thus possible to use stepped shafts 169, 171, the length of which is less than ten times the width on the ring gear 58 '.
- a breather element 130 1 can of course also be used instead of the cap, e.g. B. to improve a flow distribution.
- a twin gear which is designed similarly to the gears 1, 1 1, 1 ", 1 m, can be provided more than two vents of the previously described variants with one, two or more.
- the rear-axle drive variant of a motor vehicle 500 or 500 ′ shown as an example in FIG. 1 and FIG. 2 can also be correspondingly converted to a front-axle drive variant of a vehicle with front-axle drive.
- the drive train 3 not only does the steering movement from the steering wheel 514 reach the road wheels 510, 512 and their angular position via the steering linkage 516, but the drive train 3 also leads to the road wheels 510, 512.
- a double transmission 1 for a drive train 3 of a motor vehicle 500 with two electric machines 5, 7 is equipped with two individual transmissions 15, 17.
- the individual gears 15, 17 are two-stage spur gears with three positions 19, 21, 23 for gear centers 25, 27, 29. Two positions are occupied by input shafts 35 and output shafts 39 and represent a reference plane B.
- Position 21 for a central axis 45 as one of the gear centers 27 forms a corner of a triangle 47 resting on the reference plane B through its longest side.
- On the central axis 45 is a straight line g from one of the remaining gear centers 25, 29 forming an angle a in an angular range between 5 ° and 70 ° pullable.
- 3 'drive train in particular dual electric machine drive train
- the intermediate housing wall such as a bearing bracket, 75', 75 ", 75 gearwheel, in particular the input shaft
- first direction of rotation such as the direction of rotation at the first position, in particular
- housing 110 center, in particular of the housing, or the center area of the housing 110 'center, in particular center of a bearing opening in a bearing bracket 110 center, in particular center of a shaft, such as a hollow sleeve, in the housing
- journal area in particular journal of the first stub shaft 63 second stub shaft
- M range especially middle range
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- General Details Of Gearings (AREA)
- Gear Transmission (AREA)
Abstract
Description
Claims
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202019103770.9U DE202019103770U1 (de) | 2019-07-09 | 2019-07-09 | Doppelgetriebe mit vorteilhafter Auskragung |
DE202019103778.4U DE202019103778U1 (de) | 2019-07-09 | 2019-07-09 | Getriebe, insbesondere verblocktes Einzelradgetriebe mit Entlüftung und verringerter Gefahr des Ölaustritts |
DE202019103781.4U DE202019103781U1 (de) | 2019-07-09 | 2019-07-09 | Twin-Getriebe mit einer Doppel-Eingangswelle |
DE202019103771.7U DE202019103771U1 (de) | 2019-07-09 | 2019-07-09 | Doppelgetriebe, insbesondere für einen elektromotorischen Antriebsstrang, mit einer Stützstruktur sowie dazugehörige Lagerbrille |
PCT/EP2020/069431 WO2021005175A1 (de) | 2019-07-09 | 2020-07-09 | Doppelgetriebe |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3973210A1 true EP3973210A1 (de) | 2022-03-30 |
Family
ID=71614872
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP20740273.6A Pending EP3973210A1 (de) | 2019-07-09 | 2020-07-09 | Doppelgetriebe |
Country Status (4)
Country | Link |
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US (1) | US11865908B2 (de) |
EP (1) | EP3973210A1 (de) |
CN (1) | CN114144602A (de) |
WO (1) | WO2021005175A1 (de) |
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US11865908B2 (en) | 2019-07-09 | 2024-01-09 | Hofer Powertrain Innovation Gmbh | Dual transmission with triangularly arranged gear center positions |
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-
2020
- 2020-07-09 US US17/625,183 patent/US11865908B2/en active Active
- 2020-07-09 WO PCT/EP2020/069431 patent/WO2021005175A1/de unknown
- 2020-07-09 CN CN202080050336.2A patent/CN114144602A/zh active Pending
- 2020-07-09 EP EP20740273.6A patent/EP3973210A1/de active Pending
Also Published As
Publication number | Publication date |
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WO2021005175A1 (de) | 2021-01-14 |
US11865908B2 (en) | 2024-01-09 |
US20220281303A1 (en) | 2022-09-08 |
CN114144602A (zh) | 2022-03-04 |
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