DE102019001001B3 - Hybrid drive device - Google Patents

Abstract

The invention relates to a hybrid drive device with an internal combustion engine (11), with an electrical machine (12), with a four-shaft planetary gear (13) which has a first shaft (W1), a second shaft (W2), a third shaft (W3) and has a fourth shaft (W4), with two spur gear units (14, 15), namely a first spur gear unit (14) and a second spur gear unit (15), which has three switchable gear pairs (Z1, Z2, Z3) and three switching units (S1, S2, S3), and with at least one output shaft (W5), the internal combustion engine (11) being connected to the first shaft (W1), the electrical machine (12) being connected to the second shaft (W2), the the first spur gear part (14) is connected to the third shaft (W3), the second spur gear part (15) being connected to the fourth shaft (W4), the four-shaft planetary gear (13) having an interlocking switching unit (VK), two switching units ten (S1, S2) of the switching units (S1, S2, S3) are designed as dog clutches, wherein a switching unit (S3) of the switching units (S1, S2, S3) is designed as a multi-plate clutch, the switching unit (S3) designed as multi-plate clutch is assigned to that of the at least three gear pairs (Z3), which is intended to be engaged in an upshift to a first power-branched gear stage (G4), and wherein the first power-branched gear stage (G4) has a low overall electric machine ratio than the overall e-machine ratio of the next smaller, non-power-split gear stage (G3), the overall e-machine ratio being based on a translation starting from the electric machine (12), via the planetary gear (13) and further via the first and / or second spur gear transmission (14, 15) to the output shaft (W5) results.

Description

The invention relates to a hybrid drive device.

From the DE 10 2010 053 757 A1 is already a hybrid drive device with an internal combustion engine, with an electric machine, with a planetary gear, which has a first shaft, a second shaft, a third shaft and a fourth shaft, with two spur gear sub-transmissions, namely a first spur gear sub-transmission and a second spur gear sub-transmission, the Have at least three switchable gear pairings and at least three switching units, and with at least one output shaft, the internal combustion engine being connected to the first shaft, the electrical machine being connected to the second shaft, the first spur gear unit being connected to the third shaft, the second spur gear part is connected to the fourth shaft, the four-shaft planetary gear unit having an interlocking switching unit, wherein two switching units of the switching units are designed as dog clutches.

Furthermore, from the generic DE 10 2017 006 082 A1 a hybrid drive device is known, in addition, one of the switching units of the spur gear transmission is designed as a multi-plate clutch.

The invention is particularly based on the object of providing an advantageously compact, advantageously power-shiftable hybrid drive device. It is solved by an embodiment according to the invention according to claim 1. Further developments of the invention result from the dependent claims.

The invention is based on a hybrid drive device with an internal combustion engine, with an electric machine, with a four-shaft planetary gear, which has a first shaft, a second shaft, a third shaft and a fourth shaft, with two spur gear sub-transmissions, namely a first spur gear sub-transmission and one second spur gear unit, which, in particular at least, have three switchable gear pairs and, in particular at least, three switching units, and with at least one output shaft, the internal combustion engine being connected to the first shaft, the electrical machine being connected to the second shaft, the first Helical gear unit is connected to the third shaft, the second helical gear unit being connected to the fourth shaft, the four-shaft planetary gear unit having an interlocking switching unit, with, in particular, at least two switching units of the switching units being designed as dog clutches t are.

It is further assumed that, in particular at least, one switching unit of the switching units is designed as a multi-plate clutch.

According to the invention, it is provided that the shifting unit designed as a multi-plate clutch is assigned to that of the at least three gear pairs, which is intended to be engaged when shifting up to a power-split gear stage, and the power-split gear stage has a lower overall electric machine ratio than the E -Machine overall gear ratio of the next smaller, non-power-split gear stage, the total electric machine gear ratio resulting from a gear ratio starting from the electric machine, via the planetary gear and further via the first and / or second spur gear part to the output shaft. The spur gear sub-transmissions preferably have at least three shifting units, in particular when there are exactly three shifting units, in particular exactly one shifting unit is designed as a multi-plate clutch. At least two gear pairs, in particular exactly two gear pairs, are preferably assigned to the first spur gear unit, at least one gear pair, in particular at least two gear pairs, preferably exactly two gear pairs, to the second spur gear unit. Preferably at least two switching units, in particular exactly two switching units, are assigned to the first spur gear sub-transmission, at least one switching unit, in particular at least two switching units, preferably exactly two switching units, are assigned to the second spur gear sub-transmission. In the case of exactly three switching units, exactly two switching units are preferably designed as a dog clutch. As a result, in particular a power shift capability of the transmission of the hybrid drive device with two power paths can be reliably achieved. The power shift of a power split transmission with two power paths and a frictional shift element in the power split planetary gear is only possible if the power paths are changed. Due to the configuration according to the invention, in particular both changes in the power paths can be switched under load. At the same time, additional shafts can be dispensed with in particular, as a result of which costs and installation space can be kept low. In particular, continuous load switchability can be achieved. The planetary gear mechanism is in particular intended to bring together drive torques of the internal combustion engine and the electrical machine and to transmit them to a gear unit as a common drive torque. The planetary gear preferably comprises at least one planetary gear set. The first spur gear part transmission and the second spur gear part transmission are each preferably provided for shifting defined direct gears, with a change of gear being carried out between the spur gear part transmissions. Power-branched gear stages, which each form intermediate gears, are preferably switched between the direct gears. In particular, the direct aisles are not power-split.

The condition that determines which of the switching units must be designed as a multi-plate clutch depends on the gear ratios. It results from the condition that at least one of at least three switching units must be designed as a multi-plate clutch. If there are more than three switchable gear pairs, the fifth gear pair in particular is again provided with a switching unit designed as a multi-plate clutch. However, it would also be conceivable that the fourth gear pair is again provided with a switching unit designed as a multi-plate clutch. The condition here corresponds to that of the first multi-plate clutch.

notwendig ist. Hierfür sind insbesondere zwei Fälle möglich, wobei eine nicht leistungsverzweigten Gangstufe vor einem entsprechenden Schaltvorgang sowohl auf dem ersten Stirnradteilgetriebe als auch auf dem zweiten Stirnradteilgetriebe geschalten sein kann. Liegt die nicht leistungsverzweigte Gangstufe auf dem ersten Stirnradteilgetriebe gilt dies, wenn $$\frac{i_{02}{i}_A}{i_B+i_{02}{i}_A-i_A}>\mathrm{1,}$$

wobei i₀₂ einem Übersetzungsverhältnis einer zweiten Planetenradstufe des Planetenradgetriebes entspricht, i_A einem Übersetzungsverhältnis des ersten Stirnradteilgetriebes entspricht und i_B einem Übersetzungsverhältnis des zweiten Stirnradteilgetriebes entspricht. Liegt die nicht leistungsverzweigte Gangstufe auf dem zweiten Stirnradteilgetriebe gilt dies, wenn $$\frac{i_{02}{i}_B}{i_B+i_{02}{i}_A-i_A}>1.$$

The formation of the switching unit as a multi-plate clutch is particularly useful for switching operations from a non-power-split gear stage, such as in particular one of the gear stages G1 , G3 , G5 and G7 , with an overall electric machine ratio i _{EM, G} , to a next higher, power-split gear stage with an overall electric machine ratio i _{EM, G + 1} , which is lower than the total electric machine ratio i _{EM, G.} This means in particular that the multi-plate clutch for $${\text{i}}_{\text{EM},\text{G}+1}<{\text{i}}_{\text{EM},\text{G}}\text{f}\ddot{\text{u}}\text{r G:}=\left\{\mathrm{1,3,5}\right\}$$

necessary is. In particular, two cases are possible for this, wherein a gear stage that is not power-split can be shifted both on the first spur gear sub-transmission and on the second spur gear sub-transmission before a corresponding shift operation. If the non-power-split gear is on the first spur gear, this applies if $$\frac{i_{02}{i}_A}{i_B+i_{02}{i}_A-i_A}>\mathrm{1,}$$

where i ₀₂ corresponds to a gear ratio of a second planetary gear stage of the planetary gear, i _A corresponds to a gear ratio of the first spur gear and i _B corresponds to a gear ratio of the second spur gear. If the non-power-split gear is on the second spur gear, this applies if $$\frac{i_{02}{i}_B}{i_B+i_{02}{i}_A-i_A}>1.$$

wobei i₀₁ einem Übersetzungsverhältnis einer ersten Planetenradstufe des Planetenradgetriebes entspricht und i_FD einem Übersetzungsverhältnis eines möglichen Achsgetriebes entspricht. Eine E-Maschinen-Gesamtübersetzung i_EM entspricht bei den leistungsverzweigten Gängen $$i_{EM}=\left[\frac{1}{i_{02}}\left(i_B+i_{02}{i}_A-i_A\right)\right]i_{FD}.$$

Die Verblockungsschalteinheit des Planetenradgetriebes kann verschiedene, einem Fachmann als sinnvoll erscheinende Anordnungen und/oder Ausgestaltungen haben. Die Verblockungsschalteinheit kann insbesondere zwischen zwei beliebigen von denjenigen vier Getriebeelementen des Planetenradgetriebes angeordnet sein, die nicht ohnehin schon drehfest miteinander verbunden sind. Die Verblockungsschalteinheit ist insbesondere von einer Klauenkupplung gebildet. Unter einem „Planetenradsatz“ soll dabei insbesondere eine Einheit mit einem Sonnenrad, einem Hohlrad und mit zumindest einem von einem Planetenradträger auf einer Kreisbahn um das Sonnenrad geführten Planetenrad verstanden werden. Vorteilhafterweise weist der Planetenradsatz genau ein Standübersetzungsverhältnis auf. Unter einer „Schalteinheit“ soll insbesondere eine Einheit mit genau zwei Kopplungselementen verstanden werden, die dazu vorgesehen ist, zwei drehbar zueinander gelagerte Getriebeelemente, wie beispielsweise ein Losrad und eine Getriebeausgangswelle oder ein Losrad und eine Getriebeeingangswelle oder benachbarte Losräder unterschiedlicher Zahnradebenen schaltbar drehfest miteinander zu verbinden. Zwei benachbarte, insbesondere axial benachbarte, Schalteinheiten können dabei grundsätzlich zu einer gemeinsamen Doppelschalteinheit zusammengefasst werden, indem beispielsweise ein gemeinsames Kopplungselement für beide Schalteinheiten vorgesehen wird. Jede der Schalteinheiten kann grundsätzlich als eine rein formschlüssige Schalteinheit, beispielsweise als Klauenkupplung, als form- und reibschlüssige Schalteinheit, beispielsweise in Form einer synchronisierten Klauenkupplung, oder als eine rein reibschlüssige Schalteinheit, beispielsweise in Form einer Lamellenkupplung, ausgeführt werden. Unter „vorgesehen“ soll insbesondere speziell ausgelegt und/oder ausgestattet verstanden werden. Darunter, dass ein Objekt zu einer bestimmten Funktion vorgesehen ist, soll insbesondere verstanden werden, dass das Objekt diese bestimmte Funktion in zumindest einem Anwendungs- und/oder Betriebszustand erfüllt und/oder ausführt.This results in particular from the fact that, in the direct gears, a current total e-machine ratio i _EM corresponds to an internal combustion engine ratio i _VM , which in each case corresponds to the gear ratio of the currently switched spur gear partial transmission times a possible axle ratio. In contrast, an internal combustion engine ratio i _VM corresponds to the power-split gears $$i_{VM}=\left[i_{01}{i}_{EM}+\left(1-i_{01}\right)i_A\right]i_{FD},$$

where i ₀₁ corresponds to a gear ratio of a first planetary gear stage of the planetary gear and i _FD corresponds to a gear ratio of a possible axle gear. A total electric machine ratio i _EM corresponds to the power-split gears $$i_{EM}=\left[\frac{1}{i_{02}}\left(i_B+i_{02}{i}_A-i_A\right)\right]i_{FD}.$$

The interlocking switching unit of the planetary gear mechanism can have various arrangements and / or configurations which appear to be useful to a person skilled in the art. The interlocking switching unit can in particular be arranged between any two of those four gear elements of the planetary gear which are not already connected to one another in a rotationally fixed manner. The interlocking switching unit is in particular formed by a dog clutch. A “planetary gear set” is to be understood in particular to mean a unit with a sun gear, a ring gear and with at least one planet gear guided by a planet gear carrier on a circular path around the sun gear. The planetary gear set advantageously has exactly one gear ratio. A “switching unit” is to be understood in particular as a unit with exactly two coupling elements, which is intended to connect two rotatably mounted gear elements, such as an idler gear and a gear output shaft or an idler gear and a gear input shaft or adjacent idler gears of different gear levels, so that they can be connected in a rotationally fixed manner . Two adjacent, in particular axially adjacent, switching units can in principle be combined to form a common double switching unit, for example by providing a common coupling element for both switching units. Each of the switching units can in principle be a purely form-fitting switching unit, for example a claw coupling positive and frictional switching unit, for example in the form of a synchronized claw clutch, or as a purely frictional switching unit, for example in the form of a multi-plate clutch. “Provided” is to be understood in particular to be specially designed and / or equipped. The fact that an object is provided for a specific function should in particular be understood to mean that the object fulfills and / or executes this specific function in at least one application and / or operating state.

In this context, an “overall electric machine gear ratio” is to be understood in particular to mean a gear ratio between the electrical machine and the drive shaft, the overall gear ratio starting in particular from the electric machine, via the planetary gear unit and further via the first and / or second spur gear unit part to the output shaft. A power flow defining the overall transmission ratio can run simultaneously via the first spur gear part transmission, via the second spur gear part transmission or, in the case of power-split gear stages, via both spur gear part transmissions. In this context, a “power-split gear stage” is to be understood in particular to mean a gear stage in which torque is transmitted from the planetary gear transmission to the output shaft both partly by the first spur gear part transmission and partly by the second spur gear part transmission. Preferably, in a power-split gear stage, at least one switching unit of the first spur gear sub-transmission and one switching unit of the second spur gear sub-transmission is closed. Furthermore, in this context, a “next smaller, non-power-branched gear stage” is intended to mean, in particular, a non-power-branched gear stage that, in a proposed gear sequence, has a lowest gear stage, such as in particular one gear G1 , comes into a highest gear step, directly before the corresponding gear step, in particular power-split gear step. Preferably, the next smaller, non-power-split gear step in the intended gear sequence is followed directly by the corresponding power-split gear step.

In this context, “non-rotatably connected” is to be understood in particular to mean a connection of two, and in particular rotatably mounted, elements and / or assemblies in which the two elements and / or assemblies are arranged coaxially to one another and are connected to one another in such a way that they rotate at the same angular velocity . Furthermore, in this context, a “multi-plate clutch” is to be understood in particular as a friction clutch that has at least one first multi-plate carrier with at least one plate and at least one second multi-plate carrier with at least two plates. The at least one lamella of the first lamellar carrier is preferably arranged at least partially between the at least two lamellas of the second lamellar carrier.

It is further proposed that the two spur gear units have a fourth gear pair and a fourth gearshift unit, which is designed as a claw clutch and which is assigned to the fourth gear pair, the fourth gear pair being intended to be engaged when shifting up to a second power-branched gear stage and wherein the second power-split gear stage has a larger overall electric machine ratio than the overall electric machine gear ratio of the next smaller non-power-split gear stage. The fourth gear pair and the fourth switching unit are preferably assigned to the second spur gear transmission. In this way, power shifting between defined gear stages can be achieved in a particularly advantageous manner. In particular, an advantageously simple and reliable switching unit can be provided.

Furthermore, it is proposed that the two spur gear sub-transmissions have a further gear pair and a further switching unit, which is designed as a multi-plate clutch and which is assigned to the further gear pair, the further gear pair being intended to be engaged when shifting up to a further power-split gear stage and wherein the further power-split gear stage has a lower overall electric machine gear ratio than the overall electric machine gear ratio of the next smaller non-power-split gear stage. In particular, each switching unit that is assigned to a gear pair, which is intended to be switched on when shifting up to a further power-split gear stage and wherein the further power-split gear stage has a lower overall electric machine ratio than the overall electric machine ratio of the next smaller, non-power-split gear stage, designed as a multi-plate clutch. As a result, in particular both changes in the power paths can be switched under load. In particular, a power shift between a non-power-split gear stage in a higher power-split gear stage can be achieved, in which an overall electric machine gear ratio of the non-power-split gear stage is greater than an overall electric machine gear ratio of the power-split gear stage. In particular, continuous load switchability can be achieved.

It is further proposed that the four-shaft planetary gearbox have a first Planetary gear set and a second planetary gear set, each with three gear elements, wherein the third gear element of the first planetary gear set is rotatably connected to the third gear element of the second planetary gear set and the second gear element of the first planetary gear set is rotatably connected to the second gear element of the second planetary gear set. The first planetary gear set and / or the second planetary gear set is preferably designed as a single planetary gear set. In particular, both planetary gear sets are designed as simple planetary gear sets. The planetary gear preferably has exactly two planetary gear sets. A shaft to which the electrical machine is connected preferably connects a gear element of the first planetary gear set and a gear element of the second planetary gear set in a rotationally fixed manner. One of the two spur gear partial transmissions is preferably connected to another shaft of the planetary gear transmission, which rotatably connects another transmission element of the first planetary gear set and another transmission element of the second planetary gear set. In particular, an advantageously lockable planetary gear mechanism can thereby be provided. In this way, an advantageous power split can preferably also be achieved.

It is also proposed that the electrical machine be connected in a rotationally fixed manner to the third gear elements of the planetary gear and the first spur gear part in a rotationally fixed manner to the second gear elements of the planetary gear, or that the electrical machine be non-rotatably connected to the second gear elements of the planetary gear and the first spur gear part in a rotationally fixed manner to the third gear elements of the planetary gear connected is. The electrical machine preferably has a rotor which is connected in a rotationally fixed manner to the third gear elements of the planetary gear, and the first spur gear part is connected in a rotationally fixed manner to the second gear elements of the planetary gear. Alternatively, the rotor of the electrical machine can in particular be connected in a rotationally fixed manner to the second gear elements of the planetary gear and the first spur gear part can be connected in a rotationally fixed manner to the third gear elements of the planetary gear. In this way, an advantageous connection of the electrical machine can be achieved in particular.

Furthermore, it is proposed that the first gear elements of the planetary gear mechanism each be designed as a sun gear, the second gear elements of the planetary gear mechanism each as a planet gear carrier and the third gear elements of the planetary gear mechanism as hollow wheels. The first gear element of the first planetary gear set is preferably a sun gear, the second gear element of the first planetary gear set is a planet gear carrier, the third gear element of the first planetary gear set is a ring gear, the first gear element of the second planetary gear set is a sun gear, the second gear element of the second planetary gear set is a planet gear carrier, and the third gear element of the second planetary gear set designed as ring gears. In particular, an advantageous planetary gear mechanism can thereby be provided.

It is further proposed that the electric machine be rotatably fixed with the third gear elements of the planetary gear set designed as a ring gear, the internal combustion engine be rotatably fixed with the first gear element of the first planetary gear set designed as a sun gear, the first spur gear unit be rotatably fixed with the second gear elements of the planetary gear set designed as planet gear carriers and the second Helical gear unit is rotationally fixed with the first gear elements of the second planetary gear set designed as a sun gear. A rotor of the electrical machine is preferably non-rotatable with the third gear elements of the planetary gear mechanism, which are designed as a ring gear. The internal combustion engine preferably has a crankshaft, which is designed to rotate with the first gear elements of the first planetary gear set designed as a sun gear.

The terms “axial” and “radial” here refer in particular to a main axis of rotation of the transmission, in particular the input shafts, so that the term “axial” denotes in particular a direction that runs parallel or coaxially to the main axis of rotation. Furthermore, the term “radial” denotes in particular a direction that runs perpendicular to the main axis of rotation. A “transmission input side arrangement” is to be understood in particular to mean that the named component is arranged on a side of the further component which faces the transmission input element and / or the internal combustion engine. A “transmission output side arrangement” is to be understood in particular to mean that the named component is arranged on a side of the further component which faces away from the transmission input element and / or the internal combustion engine, even if the further component is arranged in the axial direction after the transmission output element.

Further advantages result from the following description of the figures. An exemplary embodiment of the invention is shown in the figures. The figures, the description of the figures and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into useful further combinations.

• 1 die erfindungsgemäße Hybridantriebsvorrichtung mit einem Verbrennungsmotor, mit einer elektrischen Maschine, mit einem Planetenradgetriebe und mit zwei Stirnradteilgetrieben in einer schematischen Darstellung und
• 2 eine Schalttabelle der erfindungsgemäßen Hybridantriebsvorrichtung.

Show:

• 1 the hybrid drive device according to the invention with an internal combustion engine, with an electrical machine, with a planetary gear and with two spur gearboxes in a schematic representation and
• 2nd a shift table of the hybrid drive device according to the invention.

The 1 schematically shows a hybrid drive device 10th . The hybrid drive device 10th is for a motor vehicle. The hybrid drive device 10th is for a hybrid motor vehicle. The hybrid drive device 10th has an internal combustion engine 11 on. Furthermore, the hybrid drive device 10th an electrical machine 12 on. The electrical machine 12 is on one of the internal combustion engine 11 facing side of the hybrid drive device 10th arranged.

The electrical machine 12 is next to the internal combustion engine 11 provided for generating a further drive torque. The electrical machine 12 trains an electric motor. It would also be possible to replace the electrical machine 12 to provide a hydraulic or pneumatic drive unit with a correspondingly assigned energy store. The electrical machine 12 is intended either to convert electrical energy into mechanical energy or to convert mechanical energy into electrical energy. The electrical machine points to this 12 a stator 17th and a rotor 16 on. The stator 17th is firmly connected to a body of the motor vehicle. The rotor 16 is rotatable to the stator 17th arranged. To provide and store the electrical energy, the motor vehicle has a battery device, not shown. The battery device is intended to provide electrical energy for driving the electrical machine 12 to provide and store electrical energy from the internal combustion engine 11 generated or fed from an external power grid.

The hybrid drive device 10th also has a multi-speed transmission. The hybrid drive device 10th has a planetary gear 13 on. The planetary gear 13 is for the transmission of a torque from the internal combustion engine 11 and / or from the electrical machine 12 to an output of the hybrid drive device 10th intended. The planetary gear 13 is from a four-shaft planetary gear 13 educated. The planetary gear 13 exhibits a first wave W1 , a second wave W2 , a third wave W3 and a fourth wave W4 on. The planetary gear also has 13 two planetary gear sets P1 , P2 on. The planetary gear 13 has a first planetary gear set P1 and a second planetary gear set P2 on. The first planetary gear set P1 is formed by a simple planetary gear set. The second planetary gear set P2 is formed by a simple planetary gear set. The first planetary gear set P1 has three gear elements P11 , P12 , P13 on. The second planetary gear set P2 has three gear elements P21 , P22 , P23 on. The first gear elements P11 , P21 of the planetary gear 13 are each the sun gear, the second gear elements P12 , P22 of the planetary gear 13 are each as a planet carrier and the third gear elements P13 , P23 of the planetary gear 13 are each designed as ring gears. The third gear element P13 of the first planetary gear set P1 is non-rotatable with the third gear element P23 of the second planetary gear set P2 connected and the second gear element P12 of the first planetary gear set P1 is non-rotatable with the second gear element P22 of the second planetary gear set P2 connected. Furthermore, the third gear element P13 of the first planetary gear set P1 and the third gear element P23 of the second planetary gear set P2 permanently rotatable with the rotor 16 of the electrical machine 12 coupled. The electrical machine 12 is directly on the planetary gear 13 tied up. The electrical machine 12 is non-rotatable with the third gear elements P13 , P23 of the planetary gear 13 connected. The electrical machine 12 is non-rotatable with the third gear elements designed as a ring gear P13 , P23 of the planetary gear 13 connected. The electrical machine 12 is on the second wave W2 tied up. The electrical machine 12 is about the second wave W2 to the third gear element P13 of the first planetary gear set P1 and the third gear element P23 of the second planetary gear set P2 tied up.

In general, it is particularly advantageous that the electrical machine 12 to such a shaft of the four-shaft planetary gear 13 is connected, which is one of the gear elements P11 , P12 , P13 of the first planetary gear set P1 and one of the gear elements P21 , P22 , P23 of the second planetary gear set P2 rotatably connected.

The planetary gear 13 is advantageous radially inside the rotor 16 of the electrical machine 12 arranged. The planetary gear 13 is radial inside the electrical machine 12 arranged.

The planetary gear is also advantageous 13 axially overlapping with the electrical machine 12 arranged.

Furthermore, the four-shaft planetary gear 13 an interlock switch unit VK on. The interlock switch unit VK is blocking the planetary gear 13 intended. The interlock switch unit VK is one Blocking of the first planetary gear set P1 and the second planetary gear set P2 intended.

Furthermore, the internal combustion engine 11 , in particular via a separating clutch, to the planetary gear 13 tied up. The internal combustion engine 11 is on the first wave W1 tied up. The internal combustion engine 11 is rotationally fixed with the first gear element designed as a sun gear P11 of the first planetary gear set P1 connected trained.

Furthermore, the hybrid drive device 10th two spur gearboxes 14 , 15 on. The hybrid drive device 10th has a first spur gear 14 and a second spur gear 15 on. The first spur gearbox 14 and the second spur gear 15 can be switched in parallel in a power flow. The first spur gearbox 14 and the second spur gear 15 are directly on the planetary gear 13 tied up. The second spur gearbox 15 is in an axial direction in front of the first spur gear 14 arranged. The two spur gearboxes 14 , 15 have three switchable gear pairs Z1 , Z2 , Z3 and a fourth gear pair Z4 and three switching units S1 , S2 , S3 and a fourth switching unit S4 on. The two spur gearboxes 14 , 15 have four switchable gear pairs Z1 , Z2 , Z3 , Z4 and four switching units S1 , S2 , S3 , S4 on. The gear pairs Z1 , Z2 , Z3 , Z4 are each via one of the switching units S1 , S2 , S3 , S4 switchable. The gear pairs Z1 , Z2 , Z3 , Z4 are each arranged in a gear plane. The gear pairs Z1 , Z2 , Z3 , Z4 are arranged in different gear levels. Two gear pairs Z1 , Z3 the gear pairings Z1 , Z2 , Z3 , Z4 and two switching units S1 , S3 of the switching units S1 , S2 , S3 , S4 are the first spur gearbox 14 assigned. Two gear pairs Z2 , Z4 the gear pairings Z1 , Z2 , Z3 , Z4 and two switching units S2 , S4 of the switching units S1 , S2 , S3 , S4 are the second spur gearbox 15 assigned. The gear pairs Z1 , Z2 , Z3 , Z4 each have a fixed gear, namely a first fixed gear Z11 , a second fixed gear Z21 , a third fixed gear Z31 and a fourth fixed gear Z41 and an idler gear, namely a first idler gear Z12 , a second idler gear Z22 , a third idler gear Z32 and a fourth idler gear Z42 on.

The respective fixed wheel Z11 , Z21 , Z31 , Z41 the gear pairings Z1 , Z2 , Z3 , Z4 forms an input side of the respective gear pair in the exemplary embodiment Z1 , Z2 , Z3 , Z4 while the respective idler gear Z12 , Z22 , Z32 , Z42 the gear pairings Z1 , Z2 , Z3 , Z4 one output side of each gear pair Z1 , Z2 , Z3 , Z4 forms. The fixed wheels Z11 , Z21 , Z31 , Z41 the gear pairings Z1 , Z2 , Z3 , Z4 comb each with the corresponding corresponding idler gear Z12 , Z22 , Z32 , Z42 the gear pairings Z1 , Z2 , Z3 , Z4 .

The first spur gearbox 14 has different gear ratios. The first spur gearbox 14 is rotationally fixed with the first gear element designed as a sun gear P21 of the second planetary gear set P2 educated. The first spur gearbox 14 is on the third wave W3 tied up. The first spur gearbox 14 is about the third wave W3 to the first gear element designed as a sun gear P21 of the second planetary gear set P2 tied up. The two fixed wheels Z11 , Z31 the first gear pair Z1 and the third gear pair Z3 of the first spur gear 14 are non-rotatable with the third shaft W3 connected. The drive torque is via the third shaft W3 in the first spur gearbox 14 initiated. The second spur gearbox 15 has different gear ratios. The second spur gearbox 15 is non-rotatable with the second gear elements P12 , P22 of the planetary gear 13 connected. The second spur gearbox 15 is non-rotatable with the second gear elements designed as planetary gear carriers P12 , P22 of the planetary gear 13 connected trained. The second spur gearbox 15 is on the fourth wave W4 tied up. The second spur gearbox 15 is about the fourth wave W4 on the second gear elements designed as planetary gear carriers P12 , P22 of the planetary gear 13 tied up. Furthermore, the fourth wave connects W4 the second gear elements P12 , P22 of the planetary gear 13 . The two fixed wheels Z21 , Z41 the second gear pair Z2 and the fourth gear pair Z4 of the second spur gear 15 are non-rotatable with the fourth shaft W4 connected. The drive torque is via the fourth shaft W4 in the second spur gearbox 15 initiated. In principle, however, it would also be conceivable that the electrical machine 12 non-rotatable with the second gear elements P12 , P22 of the planetary gear 13 and the second spur gear 15 non-rotatable with the third gear elements P13 , P23 of the planetary gear 13 connected is.

A driving force of the internal combustion engine becomes dependent on an engaged gear 11 and / or the electrical machine 12 from the planetary gear 13 about the third wave W3 on the first spur gear 14 and / or via the fourth wave W4 on the second spur gear 15 transfer. From the first spur gearbox 14 and / or the second spur gear transmission 15 the driving force is in turn transmitted to the drive wheels of the motor vehicle via an axle gear which is no longer visible. The axle drive can be formed, for example, by a differential.

Furthermore, the hybrid drive device 10th an output shaft W5 on. The output shaft W5 is particularly coupled to the axle drive. Furthermore, the idler gears Z12 , Z22 , Z32 , Z42 of the Gear pairs Z1 , Z2 , Z3 , Z4 each rotatable on the output shaft W5 stored. The first spur gearbox 14 has a first fixed gear Z11 the third wave W3 and a first idler gear Z12 the output shaft W5 on which comb with each other. The first spur gearbox 14 also has the second fixed gear Z21 the third wave W3 and the second idler gear Z22 the output shaft W5 on which comb with each other. Furthermore, the second spur gear transmission 15 the third fixed gear Z31 the fourth wave W4 and the third idler gear Z32 the output shaft W5 on which comb with each other. Furthermore, the second spur gear transmission 15 the fourth fixed gear Z41 the fourth wave W4 and the fourth idler gear Z42 the output shaft W5 on which comb with each other.

The spur gear partial transmissions point to a shifting of the different transmission gears 14 , 15 the hybrid drive device 10th several switching units S1 , S2 , S3 , S4 on. The hybrid drive device 10th has four switching units as an example S1 , S2 , S3 , S4 on. At least two switching units S1 , S2 , S4 of the switching units S1 , S2 , S3 , S4 are designed as dog clutches. Three switching units S1 , S2 , S4 of the switching units S1 , S2 , S3 , S4 are designed as dog clutches. At least one switching unit S3 of the switching units S1 , S2 , S3 , S4 is designed as a multi-plate clutch. A switching unit S3 of the switching units S1 , S2 , S3 , S4 is designed as a multi-plate clutch.

The first spur gearbox 14 has a first switching unit S1 of the four switching units S1 , S2 , S3 , S4 on. The first switching unit S1 is the output shaft W5 assigned. The first switching unit S1 is formed by a claw coupling. In principle, however, would also be a different design of the switching unit that appears to be useful to a person skilled in the art S1 conceivable. The first switching unit S1 is intended to be the first idler gear Z12 the first gear pair Z1 non-rotatable with the output shaft W5 connect to. The first switching unit S1 is intended to be the first idler gear Z12 the first gear pair Z1 rotatably with the actual shaft of the output shaft W5 connect to. The first switching unit S1 connects the first idler gear in a closed state Z12 the first gear pair Z1 rotatably with the actual shaft of the output shaft W5 .

The second spur gearbox 15 has a second switching unit S2 of the four switching units S1 , S2 , S3 , S4 on. The second switching unit S2 is the output shaft W5 assigned. The second switching unit S2 is formed by a claw coupling. In principle, however, would also be a different design of the switching unit that appears to be useful to a person skilled in the art S2 conceivable. The second switching unit S2 is intended to be the second idler gear Z22 the second gear pair Z2 non-rotatable with the output shaft W5 connect to. The second switching unit S2 is intended to be the second idler gear Z22 the second gear pair Z2 rotatably with the actual shaft of the output shaft W5 connect to. The second switching unit S2 connects the second idler gear in a closed state Z22 the second gear pair Z2 rotatably with the actual shaft of the output shaft W5 .

The first spur gearbox 14 has a third switching unit S3 of the four switching units S1 , S2 , S3 , S4 on. The third switching unit S3 is the output shaft W5 assigned. The third switching unit S3 is formed by a multi-plate clutch. The switching unit designed as a multi-plate clutch S3 is that of the gear pair Z3 the gear pairings Z1 , Z2 , Z3 , Z4 assigned, which is provided for an upshift to a second power-split gear stage G4 which in the exemplary embodiment from the fourth gear stage G4 is formed to be switched on, the second power-split gear stage G4 has a lower overall electric machine ratio than the overall electric machine ratio of the next smaller, non-power-split gear G3 . The overall e-machine ratio results from a translation based on the electrical machine 12 , about the planetary gear 13 and further via the first and / or second spur gear transmission 14 , 15 to the output shaft W5 . The switching units S1 , S2 , S3 , S4 are in particular always designed as a multi-plate clutch when you are shifting from a non-power-split gear, such as one of the forward gears G1 , G3 , G5 and G7 , with an overall electric machine ratio, must be shifted into a next higher, power-split gear stage with an overall electric machine ratio that is lower than the overall electric machine ratio. The third switching unit S3 For this purpose, the third idler gear is provided in this embodiment Z32 the third gear pair Z3 non-rotatable with the output shaft W5 connect to. The third switching unit S3 is intended to be the third idler gear Z32 the third gear pair Z3 rotatably with the actual shaft of the output shaft W5 connect to. The third switching unit S3 connects the third idler gear in a closed state Z32 the third gear pair Z3 rotatably with the actual shaft of the output shaft W5 .

wobei i_A dem Übersetzungsverhältnis der entsprechenden Zahnradpaarung Z1, Z3 des ersten Stirnradteilgetriebes 14, ω_W5 der Winkelgeschwindigkeit der Abtriebswelle W5 entspricht. i₀ dem Übersetzungsverhältnis der zweiten Planetenradstufe des Planetenradgetriebes 13 und i_B dem Übersetzungsverhältnis der entsprechenden Zahnradpaarung Z2, Z4 des zweiten Stirnradteilgetriebes 15 entspricht. Ist der Quotient Q kleiner als eins ist eine Lastschaltung mittels einer Klauenkupplung möglich. Ist der Quotient Q größer als eins ist eine Lamellenkupplung an der zugeschalteten Zahnradpaarung Z2, Z4 des zweiten Stirnradteilgetriebes 15 notwendig. Ausgehend von einer Gangstufe des zweiten Stirnradteilgetriebes 15 ergibt sich der Quotient wie folgt $$\Vert Q=\frac{i_B\times i_o}{i_A+i_o{i}_B-i_B}\Vert .$$

In this exemplary embodiment, the selection of the arrangement of the multi-plate clutch results in particular from a quotient of the angular velocity ω _{W2, block of} the second shaft W2 in a non-power-split gear stage divided by the angular velocity ω _{W2, split} the second shaft W2 in a next higher, power-split gear. A distinction can be made between two cases, namely from one gear level of the first spur gear 14 can be shifted into a power split gear stage or it can be from one gear stage of the second spur gear 15 be shifted into a power-split gear stage. Starting from a gear stage of the first spur gear transmission 14 the quotient is as follows $$\Vert Q=\frac{i_A\times i_O}{i_A+i_O{i}_B-i_B}\Vert ,$$

where i _{A is} the gear ratio of the corresponding gear pair Z1 , Z3 of the first spur gear 14 , ω _W5 the angular velocity of the output shaft W5 corresponds. i ₀ the gear ratio of the second planetary gear stage of the planetary gear 13 and i _B the gear ratio of the corresponding gear pair Z2 , Z4 of the second spur gear 15 corresponds. If the quotient Q is less than one, a load shift by means of a dog clutch is possible. If the quotient Q is greater than one, there is a multi-plate clutch on the connected gear pair Z2 , Z4 of the second spur gear 15 necessary. Starting from a gear stage of the second spur gear unit 15 the quotient is as follows $$\Vert Q=\frac{i_B\times i_O}{i_A+i_O{i}_B-i_B}\Vert .$$

Is the quotient Q A power shift using a dog clutch is possible less than one. If the quotient Q is greater than one, there is a multi-plate clutch on the connected gear pair Z1 , Z3 of the first spur gear 14 necessary. The third switching unit was designed accordingly S3 selected as multi-plate clutch.

The two spur gearboxes 14 , 15 have a fourth gear pair Z4 and a fourth switching unit S4 of the four switching units S1 , S2 , S3 , S4 on. The second spur gearbox 15 shows the fourth switching unit S4 on. The fourth switching unit S4 is the output shaft W5 assigned. The fourth switching unit S4 is formed by a dog clutch and the fourth gear pair Z4 assigned. The fourth gear pair Z4 is provided for an upshift to a third power-split gear stage G6 which in the exemplary embodiment from the sixth gear G6 is formed to be switched on and the second power-split gear stage G6 has a larger overall electric machine ratio than the overall electric machine ratio of the next smaller, non-power-split gear stage G5 . The fourth switching unit S4 is intended to be the fourth idler gear Z42 the fourth gear pair Z4 non-rotatable with the output shaft W5 connect to. The fourth switching unit S4 is intended to be the fourth idler gear Z42 the fourth gear pair Z4 rotatably with the actual shaft of the output shaft W5 connect to. The fourth switching unit S4 connects the fourth idler gear in a closed state Z42 the fourth gear pair Z4 rotatably with the actual shaft of the output shaft W5 .

It would also be conceivable that the two spur gear units 14 , 15 have a further gear pair and a further switching unit, which is designed as a multi-plate clutch and which is assigned to the further gear pair, the further gear pair being intended to be engaged when shifting up to a further power-branched gear stage and wherein the further power-branched gear stage has a lower E -Machine overall gear ratio than the total electric machine gear ratio of the next smaller, non-power-split gear stage. The installation of a single multi-plate clutch in the spur gear units 14 , 15 the hybrid drive device 10th , with the other switching units S1 , S2 , S4 the spur gearbox 14 , 15 Claw clutches, in particular without synchronization devices, represent in particular a sensible solution to a problem. The problem is the non-powershifting of a very specific gear change in this hybrid drive device 10th .

A switching strategy for switching the switching units S1 , S2 , S3 , S4 and the interlock switch unit VK can the table in 2nd be removed. There are seven forward gears G1 , G2 , G3 , G4 , G5 , G6 , G7 , switchable. There may be additional redundant and additional gears. A mark in the corresponding line means that the corresponding switching unit S1 , S2 , S3 , S4 and / or the interlock switch unit VK is closed in order to shift the transmission gear shown in the first column.

Reference symbol list

10th

Hybrid drive device

11

Internal combustion engine

12

machine

13

Planetary gear

14

first spur gearbox

15

second spur gear

16

rotor

17th

stator

G1

Forward gear

G2

Forward gear

G3

Forward gear

G4

Forward gear

G5

Forward gear

G6

Forward gear

G7

Forward gear

P1

first planetary gear set

P11

First gear element of the first planetary gear set

P12

Second gear element of the first planetary gear set

P13

Third gear element of the first planetary gear set

P2

second planetary gear set

P21

First gear element of the second planetary gear set

P22

Second gear element of the second planetary gear set

P23

Third gear element of the second planetary gear set

S1

First switching unit

S2

Second switching unit

S3

Third switching unit

S4

Fourth switching unit

VK

Interlocking switch unit

W1

First wave

W2

Second wave

W3

Third wave

W4

Fourth wave

W5

Output shaft

Z1

First gear pair

Z11

Fixed gear

Z12

First idler gear

Z2

Second gear pair

Z21

Fixed gear

Z22

Second idler gear

Z3

Third gear pair

Z31

Fixed gear

Z32

Third idler gear

Z4

Fourth gear pair

Z41

Fixed gear

Z42

Fourth idler gear

Claims (7)

Hybrid drive device with an internal combustion engine (11), with an electrical machine (12), with a four-shaft planetary gear (13) which has a first shaft (W1), a second shaft (W2), a third shaft (W3) and a fourth shaft ( W4) has, with two spur gear units (14, 15), namely a first spur gear unit (14) and a second spur gear unit (15), the three switchable gear pairs (Z1, Z2, Z3) with three assigned switching units (S1, S2, S3 ), and with at least one output shaft (W5), the internal combustion engine (11) being connected to the first shaft (W1), the electrical machine (12) being connected to the second shaft (W2), the first spur gear unit ( 14) is connected to the third shaft (W3), the second spur gear unit (15) being connected to the fourth shaft (W4), the four-shaft planetary gear unit (13) having an interlocking switching unit (VK), two switching units (S1, S2 ) de r switching units (S1, S2, S3) are designed as dog clutches, wherein a switching unit (S3) of the switching units (S1, S2, S3) is designed as a multi-plate clutch, characterized in that the switching unit (S3) designed as a multi-plate clutch is that of the at least one is assigned to three gear pairs (Z3), which is intended to be engaged when shifting up to a power-split gear stage (G4), and the power-split gear stage (G4) has a lower overall electric machine ratio than the electric machine gear ratio Total gear ratio of the next smaller, non-power-split gear stage (G3), the overall electric machine gear ratio resulting from a gear ratio starting from the electric machine (12), via the planetary gear (13) and further via the first and / or second spur gear part (14, 15) to the output shaft (W5). Hybrid drive device after Claim 1 , characterized in that the two spur gear units (14, 15) have a fourth gear pair (Z4) and a fourth switching unit (S4) which is designed as a claw clutch and which is assigned to the fourth gear pair (Z4), the fourth gear pair (Z4 ) is provided to be switched on when shifting up to a second power-split gear stage (G6) and the second power-split gear stage (G6) has a greater total electric machine ratio than the overall electric machine ratio of the next smaller non-power-branched gear stage (G5). Hybrid drive device after Claim 1 or 2nd , characterized in that the two spur gear units (14, 15) have a further gear pair and a further switching unit, which is designed as a multi-plate clutch and which is assigned to the further gear pair, the further gear pair being provided for an upshift to a further power-split Gear stage to be switched on and the further power-branched gear stage has a lower overall electric machine ratio than the overall electric machine gear ratio of the next smaller non-power-branched gear stage. Hybrid drive device according to one of the preceding claims, characterized in that the four-shaft planetary gear (13) has a first planetary gear set (P1) and a second planetary gear set (P2) each with three gear elements (P11, P12, P13, P21, P22, P23), wherein the third gear element (P13) of the first planetary gear set (P1) is rotatably connected to the third gear element (P23) of the second planetary gear set (P2) and the second gear element (P12) of the first planetary gear set (P1) is rotationally fixed to the second gear element (P22) of the second planetary gear set (P2) is connected. Hybrid drive device after Claim 4 , characterized in that the electrical machine (12) is rotatably connected to the third gear elements (P13, P23) of the planetary gear (13) and the second spur gear (15) is rotatably connected to the second gear elements (P12, P22) of the planetary gear (13) or the electrical machine (12) is connected in a rotationally fixed manner to the second gear elements (P12, P22) of the planetary gear (13) and the second spur gear part (15) is connected in a rotationally fixed manner to the third gear elements (P13, P23) of the planetary gear (13). Hybrid drive device after Claim 5 , characterized in that the first gear elements (P11, P21) of the planetary gear (13) each as a sun gear, the second gear elements (P12, P22) of the planetary gear (13) each as a planet carrier and the third gear elements (P13, P23) of the planetary gear ( 13) are each designed as ring gears. Hybrid drive device after Claim 6 , characterized in that the electrical machine (12) rotatably with the third gear elements (P13, P23) of the planetary gear set (13) designed as a ring gear, the internal combustion engine (11) rotatably with the first gear element (P11) of the first planetary gear set (P11) P1), the second spur gear (15) rotatably with the second gear elements (P12, P22) of the planetary gear (13) designed as a planet carrier and the first spur gear (14) rotatably with the first gear (P21) of the second planetary gear (P2) designed as a sun gear ) is trained.

Images