DE102016209068A1 - Switchable transmission - Google Patents

Abstract

A shiftable transmission for a motor vehicle for varying the transmission ratio between a transmission input (1) and a transmission output shaft (2) with a synchronization motor (8), a planetary gear with a plurality of Planetengetriebadsätzen (5, 6, 7, 16), a transmission housing (4 ), and with a plurality of torque transmitting means (10, 11, 12, 13, 14, 15), which are adapted for non-stop changing this transmission ratio, wherein the transmission input shaft (1) with a prime mover for receiving a drive power is coupled and the transmission input shaft (2 ) has a non-zero transmission input speed when the gear ratio is changed without stopping, and wherein the transmission output shaft is arranged and coupled to a wheel drive for outputting this drive power, characterized in that more than one of the torque transmitting devices (10, 11, 12, 13, 14, 15) in each case an input side (10.E, 11.E, 12.E, 13.E, 14.E, 15.E) of these with the synchronization motor (8) connected in a torque-conducting manner is such that at the standstill-free changing of the transmission ratio, the speed of the input side (10.E, 11.E, 12.E, 13.E, 14.E, 15.E) with a speed of an output side of the same torque transmitting device (10, 11, 12, 13, 14, 15), by means of the synchronization motor (8), and that a plurality of these torque transmission devices (10, 11, 12, 13, 14, 15) are designed as positive torque-transmitting devices.

Description

The invention relates to a switchable transmission according to the preamble of the first claim for a motor vehicle, such transmissions are known from the prior art, in particular from DE 197 39 906 A1 ,

The invention will be described below with reference to a motor vehicle transmission, this is not to be understood as a limitation of the invention.

In the automotive industry, a general trend is to increase the efficiency of the powertrain. The transmission as part of the powertrain is important here. Often, in such a powertrain, shiftable transmissions, i. H. Transmission in which the transmission ratio between a transmission input shaft and a transmission output shaft in discrete stages, so-called gears or grades, is changeable used. Such shiftable transmissions are often designed as so-called automatic transmissions with a combination of several Planetengetriebadsätzen. To change the gear ratio brakes and clutches, generally torque transmitting devices are provided in these transmissions, with which individual elements of the Planetengetrieberadsätze and / or the gear housing, with each other are selectively coupled.

In order to realize comfortable switching operations, these torque transmission devices are designed as frictional devices, so an overlapping control of this is possible, ie a closing of the one device and a simultaneous opening of the other. In such frictional devices incurred losses. Heat caused by frictional losses during gradual opening or closing can be dissipated by transmission oil, this transmission oil, in the opened state of the device, causes shear friction losses. Next is to actuation of the torque transmitting device, even if it is closed and remains to provide a hydraulic pressure, the provision of energy is necessary (normaly open torque transmission device).

The DE 197 39 906 A1 proposes a shiftable transmission with a plurality of Planetengetriebadsätzen and a first and a second electric drive motor. Furthermore, an internal combustion engine is provided for driving a motor vehicle. The Planetengetrieberadsätze are selectively coupled to each other by means of torque transmitting devices, so different ratios between a Getriebeeingangsund output shaft are adjustable.

It is an object of the invention to provide a shiftable transmission with improved efficiency. This object is achieved by a shiftable transmission according to the first claim, preferred developments are the subject of the dependent claims.

In the context of the invention, a switchable transmission means a stepwise change of a transmission ratio between a transmission input shaft to a transmission output shaft, so-called speed change transmission. Preferably, such a shiftable transmission has a plurality of gears for power transmission, more preferably, a continuous change of a speed ratio between a transmission input shaft and a transmission output shaft of the shiftable transmission is made possible by a rotational speed superposition within the shiftable transmission. Preferably, such a shiftable transmission for providing the translations on a planetary gear with a plurality of Planetengetriebadsätzen.

In the context of the invention, a device with a plurality of concentrically arranged gears is to be understood as an epicyclic gear, in which epicyclic so-called planetary gears are arranged, which revolve around one or more central or sun gears and further with so-called ring gears or the aforementioned central wheels or both Combing power transmission.

Preferably, in a planetary gear multiple Planetengetrieberadsätze be selectively coupled to each other, d. H. that individual elements of one Planetengetrieberadsatzes are selectively coupled to individual elements of another planetary gear set of the epicyclic gear or the same planetary gear or with a transmission housing. In particular, by this selective coupling of individual elements different transmission ratios in this switchable transmission can be displayed.

For the purposes of the invention, a planetary gear set is to be understood as a gear set having a plurality of elements, so-called gear elements, which are set up for positive power transmission. As such transmission elements or elements are to be understood in the context of the invention, a sun gear, a planet carrier for supporting at least one or a plurality of planetary gears and a ring gear. Preferably, a planetary gear set has all of the aforementioned elements, and preferably such a planetary gear set may be reduced, ie, one, about the sun gear or the ring gear such reduced Planetengetrieberadsatz does not have one of the aforementioned elements.

In this case, the so-called sun gear is designed as a central wheel, the planet gear mounted on the planet carrier or the planet gears, contact the sun gear or the ring gear or both. The ring gear is arranged concentrically to the central wheel. The planet carrier is set up for storage and guidance of the planetary gear or wheels and is arranged concentrically rotatable relative to the sun wheel or concentric with it. Such Planetengetrieberadsätze are known from the prior art and are often used in so-called automatic transmissions in automotive engineering and used in the manner described above with selective coupling, in particular to represent different ratios. In this case, friction-transmitting torque transmission devices are frequently used in known automatic transmissions.

For the purposes of the invention, a torque transmission device means a device having an input side and an output side, wherein a torque-conducting connection can be selectively produced between these sides. Further, the torque transmission device is switchable in two operating states, in a first of these operating states with this a torque transferable (torque-conducting connection made) and in the second operating state no torque from the input side to the output side can be transmitted. Such torque transmission devices are known from the prior art and are often referred to as brakes or clutches depending on their kinematics. Further, it is also known to divide such torque transmission devices with respect to their torque transmission in positive or frictional torque transmission devices. In a preferred embodiment of the invention, all torque transmission devices are designed as form-locking torque transmission devices. In a further preferred embodiment of the invention, a part of the torque transmission devices is designed as a frictional and the remainder as a form-locking torque transmission device.

For the purposes of the invention, a transmission input shaft is to be understood as a transmission shaft to which a drive power can be supplied from outside the transmission, wherein the transmission is set up to transmit this drive power to a transmission output shaft.

For the purposes of the invention, the transmission output shaft is to be understood as a transmission shaft with which at least the drive power supplied to the transmission input shaft, less unavoidable loss, can be transmitted from the transmission to a drive train, in particular in the direction of a wheel drive of a motor vehicle.

In particular, the transmission input shaft can be coupled to a primary drive machine for transmitting the drive power. Preferably, a prime mover is an energy converter, preferably an internal combustion engine or internal combustion engine.

For the purposes of the invention, the synchronization motor is to be understood as an energy converter or a drive device which is connected to the input side of one or more of the torque transmission devices such that a speed can be applied by the synchronization motor to the connected input side. Preferably, the synchronization motor is non-rotatably connectable to at least the input side of one of the torque transmitting devices, and preferably the synchronization motor is at least kinematically connectable to the input sides of one of the torque transmitting devices.

For the purposes of the invention is to be understood by the standstill-free changing the transmission ratio of the shiftable transmission, that the transmission ratio of the shiftable transmission is variable or is changed while the transmission input shaft or the transmission output shaft or both rotate. In known shiftable transmissions, this non-stop variability of the transmission ratio is achieved in that friction-fit torque transmission devices are used. In this case, such frictional torque transmission devices often have the disadvantage that for the manufacture and maintenance of the torque-conducting connection from the input side to the output side, a power must be provided and thus the efficiency of the switchable transmission is loaded.

For the purposes of the invention, a wheel drive means a driven axle or a driven wheel of a motor vehicle.

For the purposes of the invention is to be understood by synchronizing the input side with the output side of the same torque transfer device by means of the synchronization that the speed of the input side is adaptable to the speed of the output side, or that these, at least substantially, can be brought to the same speed so as to make the torque-conducting connection in particular to allow by means of the positive torque transmission device.

The shiftable transmission preferably has a multiplicity of such torque transmission devices that can be synchronized by the synchronization motor, but at least 2. The synchronisable torque transmission devices are preferably designed as positive torque transmission devices. In particular in the case of positive torque transmission devices, a torque can be transmitted from the input side to the output side of this torque transmission device by means of a positive connection and therefore particularly efficiently.

After producing the positive connection, the input side and the output side of a form-fitting torque transmission device are connected to each other in a rotationally fixed manner. Preferably, such form-fitting torque transmission devices are designed as a dog clutch or with a sliding sleeve connection.

For the purposes of the invention, the term "torque-conducting connection" is to be understood as meaning that a rotational speed can be transmitted to it by a first component, which is connected in a torque-conducting manner to a second component. In this case, a torque-conducting connection is also to be understood as a kinematic coupling of these components. With reference to the shiftable transmission, this means that the synchronization motor is also torque-conductively connected to the input side of the torque transmission device when one or more of the aforementioned Planetengetrieberadsätze are completely or partially arranged in the torque transmission direction between them and so the speed of the synchronization motor with a specific gear ratio the input side of the respective torque transmission device is transferable. In other words, the synchronization motor is also torque-conductively connected to the input side of one of the torque transmitting devices when the rotational speed is converted by the synchronization motor as it is transmitted through one or more gear stages.

In particular, a rotationally fixed connection is a subspecies of a torque-conducting connection, so that non-rotatably connected components are also connected in a torque-conducting manner. However, not every torque-conducting connection is a non-rotatable connection

For the purposes of the invention, the term rotationally fixed means that a first component, which is non-rotatably connected to a second component, is connected to it in such a way that the first and the second component have the same rotational speed and, if these are rotatably mounted, that these are mounted rotatably about the same axis of rotation. Preferably rotatably interconnected and rotatably mounted components are rotatable about a common axis of rotation when one of the components is set in motion about this axis of rotation. Further preferably, a rotationally fixed connection with a housing, in particular the transmission housing allows, according to the rotatably connected to the housing member is silent. Further preferably, a rotationally fixed connection means a torsionally rigid connection. Preferably, a non-rotatable connection is characterized in that the interconnected components are connected such that a movement transmission or a torque transmission between them is made possible without a rolling, rolling or sliding motion transmission. Further preferably, the two components rotatably connected to each other directly or indirectly contact by one or more, immovable between these other components.

In particular, through the use of a plurality of such synchronizable and in particular designed as positive torque transmission devices, torque transmitting devices, it is possible to increase the efficiency of the shiftable transmission, since no or little power is necessary for maintaining the torque-conducting connection between the input side and the output side of the positive torque transmission device ,

In a preferred embodiment, the plurality of planetary gear sets have first, second, and third planetary gear sets. Further preferably, the plurality of Planetengetriebadsätzen of these three Planetengetriebadsätzen. Further preferably, the synchronization motor is designed as an electromechanical energy converter, in particular as an electric motor. Preferably, this synchronization motor is rotatably connected to a second element of the first planetary gear set. Preferably, a third element of the first Planetengetrieberadsatzes is rotatably connected to the transmission housing. Preferably, a first element of the first Planetengetrieberadsatzes with the transmission output shaft selectively rotatably connected. Preferably, the transmission input shaft is rotatably connected to a first element of the second Planetengetrieberadsatzes. Preferably, the transmission output shaft is connected to a first element of the third planetary gear set. Further Preferably, each of the aforementioned three Planetengetrieberadsätze each have a sun gear, a planet carrier with at least one planetary gear and a ring gear on. Investigations have shown that such a connection, in particular the first planetary gear set, a particularly efficient switchable transmission can be displayed.

In a preferred embodiment of the shiftable transmission, the third element of the first planetary gear set is formed as the sun gear of this planetary gear set. Further, the second element of the first planetary gear set is formed in this embodiment of the shiftable transmission as a ring gear. In this embodiment of the shiftable transmission, the first element of the first, the second and the third Planetengetrieberadsatzes are each formed as a planet carrier with at least one planetary gear. Preferably, therefore, the ring gear of the first planetary gear set is rotatably connected to the synchronization motor.

Further preferably, the sun gear of the first Planetengetrieberadsatzes is rotatably connected to the transmission housing. Preferably, the planet carrier of the first planetary gearset is selectively rotatable connected by means of one of, in particular form-fitting, torque transmitting devices with the transmission output shaft. Further preferably, the planet carrier of the first planetary gear set is connectable with at least one element of the second planetary gear set. In particular, by such a connection of the first Planetengetrieberadsatzes a particularly efficient operation of the switchable transmission is possible.

In a preferred embodiment of the shiftable transmission, a second element of the third Planetengetrieberadsatzes is formed as a ring gear. Preferably, this ring gear with a first of these torque transmitting devices with the transmission housing selectively rotatably connected. Preferably, the first torque transmission device is designed as a positive brake. In particular, at the standstill-free changing the transmission ratio of the shiftable transmission, it is possible with respect to the first torque transmitting device, via the synchronization motor, a speed for the input side of this first torque transmitting device, which is rotatably connected to the ring gear of the third Planetengetrieberadsatzes pretend. In particular, by the described configuration of the switchable transmission is thus influenced by the synchronization motor, the speed of the input side of the first torque transmitting device and preferably this is controlled to operate the brake to speed = zero.

In a preferred embodiment of the invention, the planet carrier of the first planetary gear set is selectively rotatably connected to a second of these torque transmitting devices with the planet carrier of the third planetary gear set. Preferably, this second torque transmission device is designed as a positive coupling. In particular, by this configuration of the shiftable transmission, the first Planetengetrieberadsatzes be coupled to the third Planetengetrieberadsatzes and thus with the transmission output shaft, which in particular an efficient transmission of the drive power is enabled In a preferred embodiment of the switchable transmission of the planet carrier of the second Planetengetrieberadsatzes with a third of these torque transmission devices with a further element of the second Planetengetrieberadsatzes selectively rotatably connected. Preferably, this third torque transmission device is designed as a positive coupling. In particular, by the rotationally fixed coupling of 2 elements of the same Planetengetrieberadsatzes a blockage of this wheel is achievable and thereby driving power of this without Wälzanteil can be transferred with high efficiency.

In a preferred embodiment of the shiftable transmission with a fourth of these torque transmitting devices of the planet carrier of the third Planetengetrieberadsatzes with another element of this Planetengetrieberadsatzes selectively rotatably connected. Preferably, this fourth torque transmission device is designed as a form-locking coupling. In particular, by the rotationally fixed coupling of two elements of the same Planetengetrieberadsatzes a blocking of this set of wheels can be achieved and thereby driving power is transferable from this without Wälzanteil with high efficiency.

In a preferred embodiment of the shiftable transmission, the transmission input shaft with a fifth of these torque transmission devices selectively with one of the elements of the first planetary gear set, rotatably connected. Preferably, this fifth torque transmission device is designed as a form-locking coupling. Further preferably, the transmission input shaft by means of the fifth torque transmitting device with the ring gear of the first Planetengetrieberadsatzes selectively rotatably connected. In particular, this coupling possibility of the transmission input shaft is a particularly favorable representation of the ratios of the switchable transmission allows.

In a preferred embodiment of the shiftable transmission, a third element of the second planetary gear set and a third element of the third planetary gear set are each formed as a sun gear. Preferably, these two sun gears are rotatably connected. Further preferably, these two sun gears are rotatably connected to the input side of the fifth torque transmission device. In particular, by such a configuration of the sun gears of the second and the third Planetengetrieberadsatzes a particularly compact design of the switchable transmission is possible.

In a preferred embodiment of the shiftable transmission, a second element of the second Planetengetrieberadsatzes is formed as a ring gear. Further preferably, the ring gear of the second planetary gear set is rotatably connected to the planet carrier of the first planetary gear set. Further preferably, these two transmission elements are rotatably connected to the input side of the second torque transmission device.

In a preferred embodiment of the shiftable transmission, the planetary gear has a fourth Planetengetrieberadsatz. Preferably, this fourth Planetengetrieberadsatz, based on the geometry of the epicyclic gear, arranged in front of the first to third Planetengetrieberadsatzes, preferably on the side of the transmission input shaft. Further preferably, the switchable transmission for supplying a further drive power to a further drive motor, which is preferably coupled to this fourth Planetengetrieberadsatz or this is connectable to an element of this Planetengetrieberadsatzes.

Preferably, a first element of the fourth Planetengetrieberadsatzes with the transmission input shaft rotatably connected or is preferably rotatably connected thereto. Preferably, the further drive motor is designed as an electromechanical energy converter and preferably as an electric motor / generator and designed to provide drive power for overcoming driving resistances of a motor vehicle or in particular for synchronizing one of the torque transmission devices.

In a gear change of the transmission, so in particular a circuit from N to (N + 1) or vice versa, usually one of the torque transmitting devices remains closed. It is to be understood by closed, that a torque is transferable through this. Next, a second of the torque transmitting device is closed, which is necessary for producing the torque transmission from the transmission input shaft to the transmission output shaft in the gear to be engaged. Preferably, at the same time or with a time delay, to close this second torque transmission device, a third torque transmission device is opened, which was necessary for establishing the torque-conducting connection between the transmission input shaft and the transmission output shaft in the gear which is being designed. In such cases, the synchronization is not always possible via the synchronization motor alone (eg: in cases where the synchronization motor is torque-connected to the output through the transmission output shaft with a torque transfer device, no other torque transfer device is synchronizable by means of the synchronization motor), in such cases the further drive motor advantageous for synchronizing gears, or torque transmission devices, zoomable.

Further preferably, a second element of the fourth Planetengetrieberadsatzes the synchronization motor rotatably connected. Further preferably, a third element of the fourth Planetengetrieberadsatzes with the other drive motor torque-conducting connected.

In a preferred embodiment of the shiftable transmission, the first element of the fourth Planetengetrieberadsatzes is designed as a planet carrier with at least one planetary gear. Preferably, the second element of the fourth Planetengetrieberadsatzes is formed as a ring gear. Preferably, the third element of the fourth Planetengetrieberadsatzes is designed as a sun gear.

In a preferred embodiment of the shiftable transmission, the third element of the fourth Planetengetrieberadsatzes, preferably the sun gear of the fourth Planetengetrieberadsatzes, selectively rotatably by means of a sixth of these torque transmitting devices, connectable to the transmission housing. Preferably, the sixth torque transmission device is designed as a positive brake. In particular, by the usability of an element of the fourth Planetengetrieberadsatzes with the gearbox another translation stage for the switchable transmission is displayed.

In a preferred embodiment of the shiftable transmission is in each case an input side of several or at least in the aforementioned torque transfer devices (first to sixth torque transfer device) or in all torque transfer devices in the shiftable transmission Torque transmission devices with the synchronization motor torque conducting and preferably permanently connected.

In particular, by this torque-conducting connection of the input side of the respective torque transmitting devices with the synchronization motor, it is possible to synchronize the rotational speed of the input side with the rotational speed of the output side of the respective torque transmitting device. In particular, the synchronization of the speeds of the input and the output side of the same torque transmitting device via the synchronization motor or the other drive motor allows the use of positive torque transmission devices and with this type of torque transmission device is an increase in efficiency for the switchable transmission achievable.

Preferably, all torque transmission devices in which the input side torque-conducting is connected to the synchronization motor, designed as positive torque-transmitting devices. Preferably, the input sides of the form of a torque transfer device designed as a torque transfer means, but preferably at least 2, preferably a plurality and more preferably all of these input sides, constantly, or permanently, torque-conducting connected to the synchronization motor.

Preferably, the output sides of the aforementioned positive torque transmission device / -en, permanently, or permanently, torque-conducting connected to the transmission input shaft, the transmission output shaft or the transmission housing.

In particular, if at the transmission input shaft and the transmission output shaft, a speed is predetermined, which is different from zero (non-stationary change of the transmission ratio) is by this coupling of the positive torque transmission means of the synchronization motor or the further drive motor synchronizing the speed of the input side with the speed of the output side of this Torque transmission device allows.

Under a form-fitting torque transmission device is preferably a jaw clutch / brake or preferably a sliding sleeve connection to understand. Positive torque transfer devices as such are known in the art.

In a preferred embodiment of the shiftable transmission, the ring gear of the first planetary gear set and the ring gear of the fourth planetary gear set are rotatably connected to each other. Relative to the geometric arrangement, the fourth planetary gear set is preferably arranged in front of the first planetary gear set, that is to say in particular on the opposite side relative to the third planetary gear set.

In a preferred embodiment of the shiftable transmission, based on the geometrical arrangement of the planetary gear sets in the axial direction, in the direction from the transmission input shaft to the transmission output shaft, the first planetary gear set is disposed before the second planetary gear set and the second planetary gear set is disposed before the third planetary gear set. In particular, by such an arrangement of Planetengetrieberadsätze a particularly compact design of the switchable transmission can be achieved.

Preferably, the synchronization motor via the synchronization of the positive torque transmission devices is also set up as a motor for providing drive power for overcoming driving resistances of the motor vehicle. Further preferably, the further drive motor via the provision of a drive power for overcoming driving resistances also for the synchronization of at least one of the torque transmitting devices is set up. In particular, by this configuration, a particularly high drive power can be provided.

Embodiments and features of the invention are illustrated below with reference to the partially schematized figures, in which:

1 a longitudinal section through a switchable transmission in which the epicyclic gear consists of 3 Planetengetrieberadsätze,

2 a longitudinal section through a switchable transmission in which the epicyclic gear consists of 4 Planetengetrieberadsätze,

3 a circuit diagram for a switchable transmission, like this one in 2 is shown.

In 1 is a sectional view of a first embodiment of the switchable transmission shown. The shiftable transmission has a transmission input shaft 1 and a transmission output shaft 2 on. The drive power is provided by the transmission input shaft 1 by means of a planetary gear with 3 planetary gear sets ( 5 . 6 . 7 ) on the transmission output shaft 2 transfer. That's it Transmission ratio between the transmission shafts 1 and 2 is due to the selective coupling of different transmission elements of the planetary gear ( 5 . 6 . 7 ) by means of several positive torque transmission devices ( 10 . 11 . 12 . 13 . 14 ) changeable in discrete gear ratios.

By the synchronization motor 8th which is permanent and torque-conducting with the input sides 10.e . 11.E . 12.e . 13.E and 14.E the torque transmission devices ( 10 . 11 . 12 . 13 . 14 ), the synchronization of the rotational speed of the respective input side of the torque transmitting devices with the rotational speed of the output side is made possible. The gear topology, which is explained below, is designed so that for all Planetengetrieberadsätze by speed specification on the transmission shafts 1 . 2 and by the synchronization motor 8th , A kinematic unique state and thus the synchronization of the torque transmitting devices is made possible by the synchronization motor and thereby the use of positive torque transmission devices and thus an increase in efficiency of the switchable transmission.

At the transmission input shaft 1 For example, an internal combustion engine (not shown) is coupled, preferably by means of a torque converter or a starting clutch (not shown). When driving a motor vehicle, such an internal combustion engine is a speed for the transmission input shaft 1 in front. Also the transmission output shaft 2 rotates, as far as the motor vehicle moves, with a speed dependent on the driving speed. If, in this state, circuits are performed in the shiftable transmission, that is to say no-stop circuits, the positive torque transmission devices must be synchronized.

If now the first torque transmission device 10 , which is designed as a brake to be closed, so the speed of the input side 10.e this can be controlled to 0, since the speed of the gear housing and thus the output side of this torque transmission device 10 logically zero. About the synchronization motor 8th becomes the ring gear 5.2 of the first planetary gear set 5 driven. The sun wheel 5.3 of the first planetary gear set 5 is with the gearbox 4 rotatably connected and the synchronization motor 8th The output speed is transmitted via the planet carrier with planetary gear 5.1 of the first planetary gear set 5 on the ring gear 6.2 of the second planetary gear set 6 transfer. The planet carrier with planetary gear 6.1 of the second planetary gear set 6 is with the transmission input shaft 1 rotatably connected and rotated at the speed of this, this results in a unique speed for the sun 6.3 ,

The speed of the sun gear 7.3 of the third planetary gear set 7 corresponds to the speed of the sun gear 6.3 because they are non-rotatably connected. The speed of the planet carrier with planetary gear 7.1 of the third planetary gear set 7 is through the transmission output shaft 2 predetermined, which is coupled to the wheel drive and thereby results in a unique speed for the ring gear 7.2 of the third planetary gear set 7 , which with the input side 10.e the first torque transmitting device is rotatably connected and this speed is used to operate this by the synchronization motor 8th fixed to zero.

Also the entrance page 11.E the second torque transmitting device 11 is torque-conducting and permanent with the synchronization motor 8th connected and therefore their speed with the speed of the output side of the same torque transmitting device 11 be synchronized. The output side of the second torque transmitting device 11 is with the transmission output shaft 2 rotatably connected and has their speed. The synchronization engine 8th gives its speed over the ring gear 5.2 of the first planetary gear set 5 from. The sun wheel 5.3 This planetary gear set is with the gearbox 4 rotatably connected. The speed of the synchronization motor 8th is therefore on the planet carrier with planetary gear 5.1 transferred, this is against rotation with the input side 11.E connected and so can the speed of the input side 11.E with the output side of the same torque transmitting device 11 be synchronized.

The output side of the third torque transmitting device 12 is with the transmission input shaft 1 rotatably connected. To synchronize the speed of the input side 12.e This torque transmission device with the rotational speed of the output side gives the synchronization motor 8th in the manner described above, a speed to the planet carrier with planetary gear 5.1 off, this is with the ring gear 6.2 of the second planetary gear set 6 rotatably connected. The planet carrier with planetary gear 6.1 of the second planetary gear set 6 indicates the rotational speed of the transmission input shaft 1 on, by the speed specification on the ring gear 6.2 and the planet carrier with planetary gear 6.1 results in a unique speed for the sun 6.3 of the second planetary gear set 6 , The sun wheel 6.3 is non-rotatable with the input side 12.e the third torque transmitting device 12 connected and so can the speed of this with the speed of the output side of the same Torque transfer device 12 through the synchronization motor 8th synchronize.

Likewise, the input page 13.E the fourth torque transmitting device 13 permanent and torque-conducting with the synchronization motor 8th connected. The entrance page 13.E the fourth torque transmitting device 13 is non-rotatable with the input side 12.e the third torque transmitting device 12 connected. The output side of the fourth torque transmitting device 13 is with the transmission output shaft 2 rotatably connected. By means of the synchronization motor 8th can thus the speed of the input side 13.E the fourth torque transmitting device 13 with the rotational speed of the output side of the same torque transmitting device by the synchronization motor 8th be synchronized.

The fifth torque transmitting device 14 , or their input page 14.E is not just torque-conducting with the synchronization motor 8th connected, but even rotatable with this. The output side of the fifth torque transmitting device 14 is with the transmission input shaft 1 rotatably connected. By the synchronization motor 8th is thus a particularly easy synchronization of the speed of the input side 14.E the fifth torque transmitting device 14 allows with their output side.

In 2 is a longitudinal section of a switchable transmission with an additional fourth Planetengetrieberadsatz 16 shown. This planetary gear set 16 has a planet carrier with planetary gear 16.1 , a ring gear 16.2 and a sun wheel 16.3 on. The transmission structure concerning the synchronization motor 8th as well as the first planetary gear set 5 , the second planetary gear set 6 and the third planetary gear set 7 and the torque transfer devices (FIG. 10 . 11 . 12 . 13 . 14 ) corresponds to the already in 1 explained transmission structure.

The ring gear 16.2 of the fourth planetary gear set 16 is non-rotatable with the synchronization motor 8th connected. The sun wheel 16.3 This Planetengetrieberadsatzes is with the other drive motor 9 rotatably connected. Next is this sun wheel 16.3 rotatable with the input side 15.E the sixth torque transmitting device 15 connected, this is this torque transmission device 15 designed as a brake and the output side is rotationally fixed to the transmission housing 4 connected.

The entrance page 15.E can by means of the synchronization motor 8th be controlled at zero speed. The synchronization engine 8th gives its speed to the ring gear 16.2 of the fourth planetary gear set. The planet carrier with planetary gear 16.1 the fourth planetary gear set is non-rotatable with the transmission input shaft 1 connected and therefore has their speed. Due to the speed specification on the ring gear 16.2 and on the planet carrier 16.1 , sets a unique speed of the sun gear 16.3 one. Because the sun wheel 16.3 rotatable with the input side 15.E is connected, the speed of this is about the synchronization motor 8th adjustable.

About the further drive motor 9 In addition, drive power can be introduced into the shiftable transmission and so is a particularly simple way a hybrid drive so the interaction of the internal combustion engine, not shown, and this further drive motor 9 allows.

Hybridization is also possible via the synchronization motor alone or in addition to the further drive motor.

In 3 is a circuit diagram for eight different gear ratios or gears of the in 2 shown switchable transmission with synchronization motor 8th and another drive motor 9 shown. In this case, in the lines to be actuated to represent a gear (gear ratio) torque transmitting devices are marked by an X. An X means in the 3 shown representation that from the respective torque transmitting device, a torque transferable (positive connection between the input and output side made). The first torque transmitting device 10 and the sixth torque transmitting device 15 are provided with the suffix (Br), this is to clarify that these torque transmission devices ( 10 . 15 ) are designed as a brake.

All torque transmission devices 10 to 15 are preferably designed as positive torque-transmitting devices, since these as explained above on the synchronization motor 8th and partly via the further drive motor 9 can be synchronized. It has proven to be advantageous to use in individual gear shifts and the other drive motor for the synchronization of gears.

Regardless of other embodiments of the switchable transmission, it has been shown that individual torque transmission devices can also be designed as frictionally engaged or friction / positive torque transmission device, such as a cone synchronization, and so the Controllability of the switchable transmission is simplified. With such a design, a simplified control of the transmission is possible because not all gears must be synchronized by means of the synchronization motor or the further drive motor.

During a gear change, one of the torque transmission devices usually remains closed, while a second torque transmission device is closed and closed at the same time or with a time delay to this third torque transmission device. In such cases, the synchronization is not always possible via the synchronization motor (eg: torque transmission device 11 closed, then is the synchronization motor 8th with the transmission output shaft 2 coupled and can not synchronize any other torque transmitting device more), in such cases, the further drive motor 9 be used to synchronize gears or torque transmitting devices.

Therefore, for various switching operations also designed as an E-machine further drive motor 9 used as an additional synchronization motor.

For the gears "2" and "7" is the sixth torque transmitting device 15 pressed, this means that over the further drive motor 9 no drive power can be delivered to the shiftable transmission. An electric drive of the motor vehicle can in these cases alone via the synchronization motor 8th respectively.

In other words, the invention comprises a hybrid transmission topology, in which the synchronization motor and the further drive motor are functionally integrated in the transmission.

The transmission offers in the illustrated embodiment with four Planentenradsätzen 8-speed stages. It consists of three or four Planetengetriebadsätzen and six torque transmitting devices ( 10 - 15 ). In this case, the torque transmission devices 12 . 13 and 14 arranged so that they can each connect two elements of a Planetengetrieberadsatzes. If they are closed, then the respective planetary gear set runs in the block. The same effect can be achieved when two other elements of a planetary gearset are coupled together. These variants are to be regarded as equivalent.

• • keine Schleppverluste im offenen Zustand.
• • keine Wärmeentwicklung während der Schaltungen.
• • reduzierte Hydraulikanforderungen, da kein dauerhafter oder zumindest nur ein sehr geringer Druck zum geschlossen halten der Drehmomentübertragungseinrichtung aufgebracht werden muss.

Furthermore, the synchronization motor and the further drive motor are two electric machines ( 8th . 9 ) in the epicyclic gear ( 5 . 6 . 7 . 16 ) integrated. In the fixed translation stages, these can be used for hybrid functions. In addition, these can be used for traction-free gear changes (at least between directly adjacent gears). This makes it possible to replace the commonly used frictional torque transmission devices by positive locking. The positive torque transmission devices only take over the formation of the gait and essentially offer the following advantages:

• • no drag losses in open condition.
• • no heat generation during the circuits.
• • Reduced hydraulic requirements, since no permanent or at least only a very small pressure to hold closed the torque transmission device must be applied.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 19739906 A1 [0001, 0005]

Claims (16)

Switchable transmission for a motor vehicle for varying the transmission ratio between a transmission input ( 1 ) and a transmission output shaft ( 2 ) with a synchronization motor ( 8th ), a planetary gear with a plurality of Planetengetriebadsätzen ( 5 . 6 . 7 . 16 ), a transmission housing ( 4 ) and with a plurality of torque transmission device ( 10 . 11 . 12 . 13 . 14 . 15 ), which are adapted for non-stop changing this transmission ratio, wherein the transmission input shaft ( 1 ) can be coupled to a prime mover for receiving a drive power and the transmission input shaft ( 2 ) has a non-zero transmission input rotational speed when the transmission ratio is changed without stopping, and wherein the transmission output shaft is set up and coupled to a wheel drive for outputting this drive power, characterized in that more than one of the torque transmission devices ( 10 . 11 . 12 . 13 . 14 . 15 ) each have an input side ( 10.e . 11.E . 12.e . 13.E . 14.E . 15.E ) this with the synchronization motor ( 8th ) is torque-conductively connected, so that at the standstill-free changing of the transmission ratio, the speed of the input side ( 10.e . 11.E . 12.e . 13.E . 14.E . 15.E ) at a rotational speed of an output side of the same torque transmission device ( 10 . 11 . 12 . 13 . 14 . 15 ), by means of the synchronization motor ( 8th ), and that a plurality of these torque transmitting devices ( 10 . 11 . 12 . 13 . 14 . 15 ) are designed as form-fitting torque transmission devices. Switchable transmission according to claim 1, characterized in that the plurality of Planetengetriebadsätzen ( 5 . 6 . 7 . 16 ) a first ( 5 ), second ( 6 ) and third ( 7 ) Planetary gear set or consists of these and that the synchronization motor ( 8th ) with a second element ( 5.2 ) of the first planetary gear set ( 5 ) and that a third element ( 5.3 ) of the first planetary gear set ( 5 ) with the transmission housing ( 4 ) and that a first element ( 5.1 ) of the first planetary gear set ( 5 ) with the transmission output shaft ( 2 ) is selectively rotatable connected and that the transmission input shaft ( 1 ) with a first element ( 6.1 ) of the second planetary gear set ( 6 ) is rotatably connected and that the transmission output shaft ( 2 ) with a first element ( 7.1 ) of the third planetary gear set ( 7 ) connected is. Switchable transmission according to claim 2, characterized in that the third element ( 5.3 ) of the first planetary gear set ( 5 ) a sun gear is that the second element ( 5.2 ) of the first planetary gear set ( 5 ) is a ring gear and that the first element ( 5.1 . 6.1 . 7.1 ) of the first ( 5 ), the second ( 6 ) and the third ( 7 ) Planetengetrieberadsatzes are each a planet carrier. Switchable transmission according to one of claims 2 or 3, characterized in that a second element ( 7.2 ) of the third planetary gear set ( 7 ) is a ring gear and that this ring gear ( 7.2 ) with a first of these torque transmission devices ( 10 ) with the transmission housing ( 4 ) selectively, rotatably connected. Switchable transmission according to one of claims 2 to 4, characterized in that the planet carrier ( 5.1 ) of the first planetary gear set ( 5 ) with a second of these torque transmission devices ( 11 ) with the planet carrier ( 7.1 ) of the third planetary gear set ( 7 ) selectively, rotatably connected. Switchable transmission according to one of claims 2 to 5, characterized in that the planet carrier ( 6.1 ) of the second planetary gear set ( 6 ) with a third of these torque transmission devices ( 12 ) with another element ( 6.2 . 6.3 ) of the second planetary gear set ( 6 ) selectively, rotatably connected. Switchable transmission according to one of claims 2 to 6, characterized in that with a fourth of these torque transmission devices ( 13 ) the planet carrier ( 7.1 ) of the third planetary gear set ( 7 ) with another element ( 7.2 . 7.3 ) of this planetary gear set ( 7 ) selectively, rotatably connected. Switchable transmission according to one of claims 2 to 7, characterized in that the transmission input shaft ( 1 ) with a fifth of these torque torque transmission devices ( 14 ) with one of the elements ( 5.1 . 5.2 . 5.3 ) of the first planetary gear set ( 5 ) selectively, rotatably connected. Switchable transmission according to claim 8, characterized in that the transmission input shaft ( 1 ) with the fifth torque transmission device ( 14 ) with the ring gear ( 5.1 ) of the first planetary gear set ( 5 ) selectively, rotatably connected. Switchable transmission according to one of claims 2 to 9, characterized in that a third element ( 6.3 . 7.3 ) of the second planetary gear set ( 6 ) and the third planetary gear set ( 7 ) one sun gear each ( 6.3 . 7.3 ) and that these two sun gears ( 6.3 . 7.3 ) are rotatably connected to each other. Switchable transmission according to one of claims 2 to 10, characterized in that a second element ( 6.2 ) of the second planetary gear set ( 6 ) a ring gear ( 6.2 ) and that this ring gear ( 6.2 ) rotatably with the planet carrier ( 5.1 ) of the first planetary gear set ( 5 ) connected is. Switchable transmission according to one of the preceding claims, characterized in that the planetary gear a fourth planetary gear set ( 16 ) and a further drive motor ( 9 ) that a first element ( 16.1 ) of the fourth planetary gear set ( 16 ) with the transmission input shaft ( 1 ) rotatably connectable, that a second element ( 16.2 ) of the fourth planetary gear set ( 16 ) with the synchronization motor ( 8th ) is rotatably connectable and that a third element ( 16.3 ) of the fourth planetary gear set ( 16 ) with the further drive motor ( 9 ) is rotatably connected. Switchable transmission according to claim 12, characterized in that with a sixth of said torque transmission device ( 15 ) the third element ( 15.3 ) of the fourth planetary gear set ( 16 ) with the transmission housing ( 4 ) selectively, rotatably connected. Switchable transmission according to one of claims 12 or 13, characterized in that in all these torque transmission devices ( 10 . 11 . 12 . 13 . 14 . 15 ) each have an input side ( 10.e . 11.E . 12.e . 13.E . 14.E . 15.E ) this with the synchronization motor ( 8th ) is torque-conductively and permanently connected, so that when the standstill-free changing of the transmission ratio, the speed of this input side ( 10.e . 11.E . 12.e . 13.E . 14.E . 15.E ) at a speed of the output side of the same torque transmitting device with the synchronization motor ( 8th ) or the further drive motor ( 9 ) can be synchronized and that a plurality of these synchronizable torque transfer devices or all are designed as positive torque-transmitting devices. Switchable transmission according to one of claims 12 to 14, characterized in that the first element ( 16.1 ) of the fourth planetary gear set ( 16 ) a planet carrier is that the second element ( 16.2 ) of the fourth planetary gear set ( 16 ) is a ring gear and that the third element ( 16.3 ) of the fourth planetary gear set ( 16 ) is a sun gear. Switchable transmission according to one of claims 12 to 15, characterized in that the ring gear ( 5.2 ) of the first planetary gear set ( 5 ) and the ring gear ( 16.2 ) of the fourth planetary gear set ( 16 ) are rotatably connected to each other.

Images