DE102023002149A1 - Electric drive device for a motor vehicle, in particular for a motor vehicle - Google Patents

Abstract

The invention relates to an electric drive device (10) for a motor vehicle, with a first electric machine (12) which has a first rotor (14) and a first stator (16), with a second electric machine (18) which has a second rotor (20) and a second stator (22), with a circuit (24) common to the electric machines (12, 18) through which a coolant and/or lubricant can flow, in which the electric machines (12, 18) are arranged, which are to be cooled and/or lubricated by means of the coolant and/or lubricant, with a pump (26) arranged in the circuit (24) by means of which the coolant and/or lubricant can be conveyed through the circuit (24), with a cooling device (30) arranged in the circuit (24) downstream of the pump (26) for cooling the coolant and/or lubricant, and with a circuit (24) downstream of the cooling device (30) and the first valve device (32) arranged upstream of the electrical machines (12, 18).

Description

The invention relates to an electric drive device for a motor vehicle, in particular for a motor vehicle, according to the preamble of patent claim 1.

The DE 11 2015 007 075 T5 is known an electric rotary machine cooling structure, wherein a coolant is supplied by a pump to a stator and a rotor of an electric rotary machine, whereby the stator and the rotor are cooled.

The object of the present invention is to provide an electric drive device for a motor vehicle, so that a particularly advantageous supply of electrical machines in the electric drive device can be realized in a particularly cost-effective manner.

This object is achieved by an electric drive device with the features of patent claim 1. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

The invention relates to an electric drive device, also referred to as an electric drive system, for a motor vehicle, also referred to simply as a vehicle. This means that the motor vehicle, preferably designed as a motor vehicle, in particular a passenger car, has the electric drive device in its fully manufactured state and can be driven by means of the electric drive device, in particular purely electrically. For example, in its fully manufactured state the motor vehicle has at least or exactly two vehicle axles, also referred to simply as axles, arranged one after the other in the longitudinal direction of the motor vehicle and thus one behind the other. The respective vehicle axle has, for example, at least or exactly two vehicle wheels, also referred to simply as wheels. For example, the vehicle wheels of the respective vehicle axle are arranged on opposite sides of the motor vehicle in the transverse direction of the motor vehicle. The vehicle wheels are ground contact elements by means of which the motor vehicle is or can be supported downwards on a ground in the vertical direction of the motor vehicle. If the motor vehicle is driven along the ground while the motor vehicle is supported on the ground in the vertical direction of the motor vehicle via the ground contact elements, the vehicle wheels roll, in particular directly, on the ground. For example, the vehicle wheels of at least or exactly one of the vehicle axles can be driven, in particular purely electrically, by means of the electric drive device, as a result of which the motor vehicle as a whole can be driven, in particular purely electrically. The vehicle wheels that can be driven by means of the electric drive device are also referred to as driven wheels, drivable wheels or drive wheels. When reference is made below to the vehicle wheels or the wheels, this means the drive wheels, unless otherwise stated.

The electric drive device has a first electric machine, which is also referred to as a first electric machine. The first electric machine has a first rotor and a first stator. For example, the first rotor can be driven by means of the first stator and can therefore be rotated about a first machine axis of rotation relative to the first stator. In particular, the first electric machine can provide first drive torques via the first rotor, by means of which the motor vehicle can be driven, in particular purely electrically. The electric drive device also has a second electric machine, which is provided in particular in addition to the first electric machine and has a second stator and a second rotor. For example, the second rotor can be driven by means of the second stator and can therefore be rotated about a second machine axis of rotation relative to the second stator. The electric machines are preferably arranged coaxially to one another, so that the machine axes of rotation coincide. In particular, the second electric machine can provide second drive torques via its second rotor, by means of which the motor vehicle can be driven, in particular purely electrically.

The electric drive device also has a circuit, also simply referred to as a circuit, through which a preferably liquid coolant and/or lubricant can flow. The coolant and/or lubricant is also referred to as a fluid. When the fluid is mentioned in the following, this is to be understood as the coolant and/or lubricant, unless otherwise stated. The fluid is preferably a liquid. The fluid is most preferably an oil. For example, the fluid can be part of the electric drive device. The circuit is a circuit common to the electric machines, since the electric machines are arranged in the circuit. This allows the electric machines to be supplied with the fluid by means of the circuit, i.e. via the circuit. In other words, the fluid can be fed to the electric machines by means of the circuit. The electric machines can be supplied with the fluid (coolant and/or lubricant) by means of the fluid (coolant and/or lubricant). the lubricants) are cooled and/or lubricated.

A pump is arranged in the circuit, by means of which the fluid can be conveyed through the circuit. The pump can thus be used, for example, to convey the fluid to the electrical machines. The pump is preferably an electrically operated pump, i.e. an electric pump.

The electric drive device also has a cooling device arranged in the circuit downstream of the pump and in particular upstream of the electric machines, by means of which the fluid can be cooled. For example, the cooling device can be flowed through by the fluid. Furthermore, for example, a coolant can flow around and/or through the cooling device. For example, heat can be transferred from the fluid to the coolant via the cooling device, thereby cooling the fluid. Thus, for example, the cooling device is designed as a heat exchanger. For example, the medium is a liquid or a gas, thus a liquid or gaseous medium.

The electric drive device also has a first valve device, which is arranged in the circuit downstream of the cooling device and upstream of the electric machines. The valve device can be used to adjust the supply of the electric machine with the coolant and/or lubricant conveyed by the pump and thus provided by the pump. For example, the first valve device can be used to adjust the distribution of the coolant and/or lubricant conveyed by the pump and thus provided by the pump between a supply flow of the coolant and/or lubricant that is supplied or can be supplied to the first rotor and is designed, for example, as a volume flow, and a supply flow of the coolant and/or lubricant that is supplied or can be supplied to the first stator and is designed, for example, as a volume flow. In particular, it is conceivable that the fluid conveyed by the pump and thus provided by the pump can be supplied to either the first rotor or the first stator using the first valve device.

In order to be able to supply the electrical machines with the fluid conveyed by the pump in a particularly cost-effective and efficient manner, the invention provides that the second stator in the circuit is connected in a fluidically parallel manner to the first stator, wherein the second stator and the first stator can be supplied with the coolant and/or lubricant (fluid) conveyed by the pump via the first valve device. In addition, the invention provides that the second rotor in the circuit is connected in a fluidically parallel manner to the first rotor, wherein the second rotor and the first rotor can be supplied with the coolant and/or lubricant conveyed by the pump via the first valve device. Thus, for example, the first stator and the second stator are arranged in a first flow path of the circuit through which the fluid conveyed by the pump can flow, and for example, the first rotor and the second rotor are arranged in a second flow path of the circuit through which the fluid conveyed by the pump can flow. The flow paths are also simply referred to as paths or flow branches. The first stator and the second stator are connected in parallel to one another in the first flow path in terms of flow technology, and the first rotor and the second rotor are connected in parallel to one another in the second flow path in terms of flow technology. Thus, for example, the first stator and the second stator form a stator pair arranged in particular in the first flow path, and the first rotor and the second rotor form a rotor pair arranged in particular in the second flow path. The feature that a supply of the electrical machine with the fluid conveyed by the pump can be adjusted by means of the first valve device is to be understood, for example, in particular as follows: For example, the fluid conveyed by the pump and thus provided by the pump can be supplied optionally to the first flow path and thus to the stator pair, thus the stators, or to the second flow path and thus to the rotor pair, thus the rotors, by means of the first valve device. For this purpose, for example, the first valve device can be switched between at least or exactly two switching states, namely a first switching state and a second switching state. In the first switching state, for example, the first flow path is fluidically connected to the pump via the first valve device, in particular while the second flow path is fluidically separated from the pump by means of the first valve device. Thus, with respect to the flow paths, only the first flow path can be supplied with the fluid conveyed by the pump via the first valve device, so that with respect to the stator pair and the rotor pair, only the stator pair can be supplied with the fluid conveyed by the pump via the valve device.

In the second switching state, for example, the second flow path is fluidically connected to the pump via the first valve device, in particular while the second flow path is fluidically separated from the pump by means of the first valve device. Thus, with respect to the Flow paths, only the second flow path can be supplied with the fluid pumped by means of the pump via the first valve device, so that with respect to the stator pair and the rotor pair, only the rotor pair can be supplied with the fluid pumped by means of the pump via the first valve device.

If the pump is thus operated so that the fluid is conveyed by means of the pump while the first valve device is in the first switching state, then, with respect to the flow paths, only the first flow path is supplied with the fluid conveyed by means of the pump via the first valve device, so that, with respect to the stator pair and the rotor pair, only the stator pair is supplied with the fluid conveyed by means of the pump via the first valve device, while the rotor pair, and thus the rotors, are not supplied with the fluid conveyed by means of the pump via the first valve device. If the pump is operated so that the fluid is conveyed by means of the pump while the first valve device is in the second switching state, then, with respect to the flow paths, only the second flow path is supplied with the fluid conveyed by means of the pump via the first valve device, so that, with respect to the stator pair and the rotor pair, only the rotor pair is supplied with the fluid conveyed by means of the pump via the first valve device, while the stator pair, and thus the stators, are not supplied with the fluid conveyed by means of the pump via the first valve device.

Furthermore, it is conceivable, for example, that by means of the first valve device, in particular in a third switching state of the first valve device, a total flow of the fluid, for example designed as a volume flow and formed by the fluid conveyed by the pump, can be or is divided, namely into a first partial flow, which is larger than zero, for example designed as a volume flow, and a second partial flow, which is larger than zero, for example designed as a volume flow, for example, with the partial flows, for example, adding up to the total flow. By means of the first valve device, i.e. via the first valve device, for example, the first partial flow is guided to and into the first flow path and thus fed to the stator pair, and therefore to the stators, and by means of the first valve device and thus via the first valve device, for example, the second partial flow is introduced to and into the second flow path.

Since the stators in the first flow path are connected in parallel to one another in terms of flow, the first partial flow can be divided into a first sub-flow, for example, designed as a volume flow, and a second sub-flow, for example, designed as a volume flow. The first sub-flow can be fed to the first stator, for example, and the second sub-flow can be fed to the second stator, for example, whereby the stators can be supplied with the fluid. For example, the first sub-flow and the second sub-flow together make up the first partial flow. The second partial flow can be divided into a third sub-flow, in particular designed as a volume flow, and a fourth sub-flow, for example, designed as a volume flow, whereby the third sub-flow and the fourth sub-flow make up the second partial flow. For example, the third partial flow can be fed to the first rotor and the fourth partial flow to the second rotor, so that the rotors can be supplied with the fluid. The same can be applied to the first switching state and the second switching state. In the first switching state, the fluid conveyed by the pump and introduced into the first flow path via the valve device is divided into a first supply stream, for example in the form of a volume flow, and a second supply stream, for example in the form of a volume flow, wherein the first supply stream can be or is supplied to the first stator and the second supply stream to the second stator. In this way, the stators can be supplied with the fluid in the first switching state. In the second switching state, for example, the fluid conveyed by the pump and introduced into the second flow path by the valve device can be divided into a third supply stream, for example in the form of a volume flow, and a fourth supply stream, for example in the form of a volume flow. The third supply stream can be supplied to the first rotor, for example, and the fourth supply stream can be supplied to the second rotor, for example, whereby the rotors can be supplied with the fluid. The invention thus enables the realization of an efficient cooling and/or lubrication system, by means of which the electrical machines can be supplied with the fluid efficiently and as needed and in a particularly cost-effective manner, in order to be able to cool and/or lubricate the electrical machines efficiently, effectively, as needed and in a cost-effective manner. Overall, it can be seen that the rotors and the stators are drive elements of the electrical drive device. The invention enables a particularly advantageous supply, in particular a variable and thus demand-oriented supply, of the four drive elements. (first rotor, first stator, second rotor, second stator) with the coolant and/or lubricant.

In particular, the cooling circuit enables the drive elements to be supplied with the fluid as needed, whereby the drive elements can be supplied with the fluid at least substantially independently of one another and thus cooled and/or lubricated.

It can also be seen that the invention provides for a fundamental separation or division into a supply of the stators with the fluid and a supply of the rotors with the fluid. The background to this is in particular that the stators are different from the rotors in terms of the system. In particular, the invention can make it possible to set a first flow of the coolant and/or lubricant for the stator pair, also referred to as the stator system, for example, in the form of a volume flow and also referred to as the first flow, in particular compared to a second flow of the coolant and/or lubricant for the rotor pair, also referred to as the rotor system, for example, in the form of a volume flow and also referred to as the second flow.

In a particularly advantageous embodiment of the invention, a second valve device is arranged in the circuit downstream of the first rotor, downstream of the first stator, upstream of the second rotor and upstream of the second stator, which is thus arranged, for example, in the first flow path and in the second flow path. The second valve device can be used to adjust the supply of the second rotor and the second stator with the coolant and/or lubricant conveyed by the pump and thus provided by the pump. This makes it possible to achieve a particularly needs-based and thus effective and efficient supply of the electrical machines, in particular the second stator and the second rotor and subsequently, for example, also the first rotor and the first stator, in a particularly simple, cost-effective manner.

It has proven to be particularly advantageous if the second valve device can be switched between a supply state and a separation state. In the supply state, the second rotor and the second stator can be supplied with the coolant and/or lubricant delivered by the pump via the second valve device. If, for example, the first valve device is closer to the switching state and the second valve device is closer to the supply state, the first stator can be supplied with the fluid delivered by the pump via the first valve device, and the second stator can be supplied with the fluid delivered by the pump via the second valve device and the first valve device. If, for example, the first valve device is in its second switching state and the second valve device is in its supply state, the first rotor can be supplied with the fluid delivered by the pump via the first valve device, and the second rotor can be supplied with the fluid delivered by the pump via the second valve device and the first valve device. In the separated state, the supply of the coolant and/or lubricant delivered by the pump to the second rotor and the second stator via the second valve device is prevented, for example in such a way that in the separated state the second rotor and the second stator are fluidically separated from the pump, in particular from the first valve device, by means of the second valve device. If, for example, the first valve device is in the first switching state, the first stator can indeed be supplied with the fluid delivered by the pump via the first valve device, but the second stator is not supplied with the fluid delivered by the pump, and in particular the first rotor and the second rotor are also not supplied with the fluid delivered by the pump. If, for example, the first valve device is in its second switching state while the second valve device is in its separation state, the first rotor is supplied with the fluid conveyed by the pump via the first valve device, but the second rotor is not supplied with the fluid conveyed by the pump and, in particular, the first stator and the second stator are also not supplied with the fluid conveyed by the pump.

This means that a flow of coolant and/or lubricant supplied or capable of being supplied to the second rotor and the second stator can be selectively switched on or off by means of the second valve device. This makes it particularly easy to supply the electrical machine in a way that is appropriate to requirements and therefore efficient and effective.

In order to be able to implement a particularly needs-based and thus effective and efficient supply of the electrical machines with the coolant and/or lubricant in a particularly simple manner and in particular to be able to adjust and thus vary it, it is provided in a further embodiment of the invention that the second valve device is designed to control several values, different from 0 and in particular larger than 0, of a respective value supplied via the second valve device. to set the fluid flow of the coolant and/or lubricant to be supplied to the second rotor and the second stator, which is formed by the coolant and/or lubricant conveyed by the pump and in particular is designed as a volume flow. In other words, if, for example, the pump conveys the coolant and/or lubricant (fluid) while the first valve device is in its first switching state, the fluid conveyed by the pump forms the fluid flow mentioned, which flows to the second valve device, in particular via the first valve device. The second valve device can now set the multiple values of the fluid flow, which are different from one another and in particular different from 0, in particular larger than 0, and which can be or is supplied to the second stator via the second valve device. This makes it possible to supply the second stator and in particular also the first stator with the fluid in a particularly needs-based manner, in particular because the respective value of the fluid flow or the setting of the respective value of the fluid flow can influence the supply of the first stator with the fluid conveyed by the pump.

If, for example, the pump delivers the fluid while the first valve device is in the second switching state, the fluid delivered by the pump forms the aforementioned fluid flow, which flows, in particular via the first valve device, to the second valve device. The second valve device can now set the multiple values of the fluid flow that are different from one another and different from 0, in particular larger than 0, and which can be or is fed to the second rotor via the second valve device. This makes it possible to achieve a particularly advantageous and needs-based and therefore effective and efficient supply of the second rotor and, for example, also the first rotor with the fluid, since, for example, the respective value of the fluid flow or the setting of the respective value of the fluid flow can influence the supply of the first rotor with the fluid delivered by the pump.

In the case of electric drives comprising two electric machines, in which cooling and/or lubrication of one of the electric machines is of greater importance than cooling and/or lubrication of the other electric machine, the present invention is particularly advantageous since the fluid conveyed by means of the pump or a volume flow resulting therefrom can, for example, first be supplied to one electric machine, in particular the first electric machine, and then or thereafter a volume flow of the fluid formed by the fluid conveyed by means of the pump to the other electric machine, in particular to the second electric machine, can be adjusted in particular by means of the second valve device.

For example, the second valve device can be designed as a control solenoid valve. In other words, the second valve device can be switched into intermediate switching states that differ from the first switching state and the second switching state, in particular by electrically or electronically controlling the second valve device, whereby intermediate values of the fluid flow that differ from zero and a maximum fluid flow can be set.

In order to be able to supply the second rotor and the second stator with the fluid in a particularly simple and cost-effective manner, it is provided in a further embodiment of the invention that the second valve device is designed as a hydraulically actuated, thus hydraulically actuated valve device, whereby the fluid flow, thus the respective value of the fluid flow, is dependent on a pressure, in particular a static pressure, prevailing in a branch of the circuit leading from the first stator to the second valve device downstream of the first stator.

Another example is characterized in that the circuit has a first supply branch assigned to the first rotor, via which the coolant and/or lubricant delivered by the pump can be fed to the first rotor in order to supply the first rotor with the coolant and/or lubricant delivered by the pump. The circuit has a second supply branch assigned to the second rotor and connected in terms of flow parallel to the first supply branch, via which the coolant and/or lubricant delivered by the pump can be fed to the second rotor in order to supply the second rotor with the coolant and/or lubricant delivered by the pump. A first check valve device is arranged in the first supply branch and is connected in terms of flow to the second rotor and in terms of flow parallel to the second supply branch, by means of which a backflow of coolant and/or lubricant away from the first rotor can be prevented, in particular automatically. In the second supply branch, a second check valve device is arranged, which is connected in a fluidic parallel manner to the first rotor, in a fluidic parallel manner to the first supply branch and in a fluidic parallel manner to the first check valve device, by means of which a return-flowing cooling and/or lubricant away from the second rotor can be prevented, in particular automatically. For example, it is provided that the first check valve device opens, in particular automatically, in the direction of the first rotor and opens, in particular automatically, in an opposite direction pointing away from the first rotor. The first check valve device thus releases the first supply branch, in particular automatically, for a flow of the fluid towards the first rotor, wherein, for example, the first check valve device fluidically blocks the first supply branch for an opposite flow of the fluid away from the first rotor, in particular automatically. Accordingly, it is preferably provided that the second check valve device opens, in particular automatically, towards the second rotor and blocks in the opposite direction pointing away from the second rotor, in particular automatically. Thus, it is preferably provided that the second check valve device releases the second supply branch for a flow of the fluid towards the second rotor, in particular automatically, wherein, for example, the second check valve device fluidically blocks the second supply branch for an opposite flow of the fluid away from the second rotor, but automatically. As a result, unfavorable flows of the fluid can be avoided in a simple and cost-effective manner, so that a particularly advantageous supply of the electrical machines with the fluid can be achieved. In one embodiment of the invention, it is provided that the second check valve device is designed differently than the first check valve device, so that in particular an opening pressure of the first check valve device is different from the opening pressure of the second check valve device, or, or in addition a volume flow through the first check valve device is different from a volume flow through the second check valve device.

A further embodiment is characterized in that the circuit has a branching point downstream of the pump, upstream of at least one of the rotors and upstream of at least one of the stators, at which the coolant and/or lubricant conveyed by the pump and thus provided by the pump flows into a supply branch of the circuit, via whose supply branch the at least one rotor and the at least one stator connected in parallel to the at least one rotor can be supplied with the coolant and/or lubricant conveyed by the pump, a first fluid flow of the coolant and/or lubricant and a second fluid flow of the coolant and/or lubricant flowing to at least one consumer branch of the circuit leading to parallel consumers. This ensures that both the electrical machines and the parallel consumer are supplied with the fluid in a particularly simple manner and in a particularly needs-based, efficient and effective manner.

In a further, particularly advantageous embodiment of the invention, it is provided that the branching point is arranged downstream of the first valve device, upstream of the at least one rotor and upstream of the at least one stator in the circuit. This can ensure a particularly advantageous, efficient and cost-effective guidance of the fluid.

In order to be able to realize a particularly advantageous guidance of the fluid, it is provided in a further embodiment of the invention that the branching point is arranged downstream of the pump and upstream of the cooling device.

In a further embodiment of the invention, a reservoir is provided for at least temporarily holding the coolant and/or lubricant. For example, the reservoir is a tank or a reservoir also referred to as a coolant and/or lubricant reservoir.

It has proven to be particularly advantageous if the circuit has a first supply line assigned to the second stator, via which the coolant and/or lubricant conveyed by the pump can be fed to the second stator in order to supply the second stator with the coolant and/or lubricant conveyed by the pump 6. For example, the aforementioned second supply branch is part of the first supply line. Furthermore, the circuit has a second supply line assigned to the second rotor, via which the coolant and/or lubricant conveyed by the pump can be fed to the second rotor in order to supply the second rotor with the coolant and/or lubricant conveyed by the pump. In this case, a valve element is arranged in the circuit downstream of the first rotor and downstream of the second rotor, by means of which the supply lines can be fluidically connected to the reservoir or fluidically separated from the reservoir. This means that a respective return flow volume of the fluid from the respective supply line can be switched on or off as required using the valve. This means that the electrical machine can be supplied with the fluid in a particularly cost-effective and demand-oriented manner.

Another embodiment is characterized by the fact that the pump has a Reservoir has a suction connection arranged, wherein the first stator and the first rotor each have a return connection for a return of the coolant and/or lubricant into the reservoir. This can ensure a demand-oriented, effective and efficient conduction of the fluid.

In a further embodiment of the invention, the first valve device can be switched to the separation state. In the separation state, the electrical machines are fluidically separated from the pump by means of the first valve device, whereby in the separation state a volume flow of the coolant and/or lubricant from the pump to the electrical machine is prevented by means of the first valve device. Thus, by or in the separation state, a volume flow of the fluid, in particular from the pump to the electrical machine, can be switched off or is switched off. This makes it possible to provide the electrical machines with the fluid in a particularly needs-based and therefore effective and efficient manner in a cost-effective manner.

In a further embodiment of the invention, a hydraulic valve and an orifice arranged upstream of the hydraulic valve and downstream of the parallel consumer are provided in the consumer branch of the circuit leading to the at least one parallel consumer upstream of the parallel consumer. The hydraulic valve has a valve piston, with a first pressure force resulting from a first control pressure derived downstream of the hydraulic valve and upstream of the orifice acting on the valve piston on the one hand and a spring force on the other. A direction of action of the spring force is opposite to a direction of action of the first pressure force. In addition, a second pressure force acts on the valve piston, which results from a second control pressure derived downstream of the orifice and which is in the same direction as the spring force. Advantageously, with this embodiment of the invention, particularly in a design of the cooling circuit without the second valve device, a temperature-independent distribution of the coolant and lubricant between the electric machines and the parallel consumer is possible, and an oversupply of the parallel consumer with coolant and lubricant can be avoided, while at the same time the cooling circuit is technically simple.

In a further embodiment of the invention, it is provided that the electric drive device has self-holding claw switching elements for connecting and disconnecting the first electric machine and/or the second electric machine, so that cooling and lubricating agents are only required for a short time to actuate the claw switching elements.

Finally, in a further embodiment of the invention, the drive device according to the invention has only one, that is to say exactly one and thus a single gear stage and the cooling/lubrication of transmission components plays a subordinate role, since the number of gears is small and switching elements can be omitted or kept to a small number.

Further advantages, features and details of the invention emerge from the following description of preferred embodiments and from the drawing. The features and combinations of features mentioned above in the description as well as the features and combinations of features mentioned below in the description of the figures and/or shown alone in the figures can be used not only in the respective combination specified, but also in other combinations or on their own, without departing from the scope of the invention.

• 1 eine schematische Darstellung einer ersten Ausführungsform einer elektrischen Antriebseinrichtung für ein Kraftfahrzeug;
• 2 eine schematische Darstellung einer zweiten Ausführungsform der Antriebseinrichtung;
• 3 eine schematische Darstellung einer dritten Ausführungsform der Antriebseinrichtung;
• 4 eine schematische Darstellung einer vierten Ausführungsform der Antriebseinrichtung; und
• 5 eine schematische Darstellung einer vierten Ausführungsform der Antriebseinrichtung.

The drawing shows in:

• 1 a schematic representation of a first embodiment of an electric drive device for a motor vehicle;
• 2 a schematic representation of a second embodiment of the drive device;
• 3 a schematic representation of a third embodiment of the drive device;
• 4 a schematic representation of a fourth embodiment of the drive device; and
• 5 a schematic representation of a fourth embodiment of the drive device.

In the figures, identical or functionally identical elements are provided with identical reference symbols.

1 shows a schematic representation of a first embodiment of an electric drive device 10, also referred to as an electric drive system, for a motor vehicle, also referred to simply as a vehicle. This means that the motor vehicle, preferably designed as a motor vehicle, in particular as a passenger car, has the electric drive device 10 in its fully manufactured state and can be driven by means of the electric drive device 10, in particular purely electrically. The electric drive device 10 has a first electric machine 12, which has a first rotor 14 and a first stator 16. The rotor 14 can be driven by means of the stator 16 and can thereby rotate, for example, about a first machine axis of rotation relative to the stator 16. bar. The electric drive device 10 also has a second electric machine 18, which has a second rotor 20 and a second stator 22. For example, the stator 22 can drive the rotor 20 and thereby rotate it about a second machine axis of rotation relative to the stator 22. The electric machines 12 and 18, which are also referred to as electric machines, are preferably arranged coaxially to one another so that the machine axes of rotation coincide. The electric drive device 10 also has a circuit 24, also simply referred to as a circuit, through which a preferably liquid coolant and/or lubricant can flow. The coolant and/or lubricant is a fluid, which is preferably a liquid, in particular an oil. When the fluid is mentioned above and below, this is to be understood as the coolant and/or lubricant, unless otherwise stated. The drive device 10 has a pump 26 arranged in the circuit 24, by means of which the fluid can be conveyed through the circuit 24. The pump 26 is preferably an electric pump, and therefore an electrically operated pump. For this purpose, the pump 26 has, for example, a conveying element 27 and a motor 29, which is designed, for example, as an electric motor. For example, the conveying element 27 is arranged in a pump housing of the pump 26, wherein the conveying element 27 is, for example, movable, in particular rotatable, relative to the pump housing. By moving, in particular rotating, the conveying element 27 relative to the pump housing, the fluid can be conveyed by means of the conveying element 27 and thus by means of the pump 26 and in particular conveyed through the circuit 24. The conveying element 27 can be driven by means of the motor 29 and can therefore be moved, in particular rotatable, relative to the pump housing. The drive device 10 also has a cooling device 30, which is arranged in the circuit 24 and downstream of the pump 26 and preferably upstream of the electrical machines 12 and 18. The fluid can be cooled by means of the cooling device 30. For example, the fluid can flow through the cooling device. Furthermore, for example, the cooling device 30 can be flowed through and/or around by a medium, in particular a liquid or gaseous medium. For example, heat can be transferred from the fluid to the medium via the cooling device 30, thereby cooling the fluid. Thus, for example, the cooling device 30 is designed as a heat exchanger. The electrical drive device 10 also has a first valve device 32 arranged in the circuit 24 downstream of the pump 26 and downstream of the cooling device 30, via which the electrical machines 12 and 18 can basically be supplied with the fluid conveyed by means of the pump 26. In this case, the first valve device 32 can be used to adjust the supply of the electrical machines 12 and 18 with the fluid (coolant and/or lubricant) conveyed by the pump 26 and thereby provided by the pump 26. In 1 V1 designates a first embodiment of the first valve device 32, also referred to as a first variant or first construction variant, and V2 designates a second embodiment of the first valve device 32, also referred to as a second variant or second construction variant.

The valve device 32, in particular the first embodiment V1 of the first valve device 32, can be switched, for example, between at least or exactly two switching states, namely a first switching state Z1 and a second switching state Z2, in particular by electrically or electronically controlling the valve device 32. The second embodiment V2 of the first valve device 32 can be switched, for example, between at least or exactly three switching states, namely the first switching state Z1, the second switching state Z2 and a third switching state Z3, which is, for example, a disconnected state of the first valve device 32. In particular, the valve device 32 can be switched between the switching states Z1 and Z2 or between the switching states Z1, Z2 and Z3 by electrically or electronically controlling the valve device 32. For this purpose, for example, the first valve device 32 has a first valve part which is movable, for example, in particular relative to a first valve housing of the first valve device 32, between a first switching position causing the first switching state Z1 and a second switching position causing the second switching state Z2, in particular translationally and/or rotationally, in particular with regard to the first embodiment V1. With regard to the second embodiment V2, the first valve part is movable, for example, in particular relative to the valve housing, between the first switching position causing the first switching state Z1, the second switching position causing the second switching state Z2 and a third switching position causing the third switching state Z3, in particular translationally and/or rotationally.

Out of 1 It can be seen that in the circuit 24 the second stator 22 is connected in a fluidic manner parallel to the first stator 16, whereby the stators 16 and 22 can be supplied with the fluid conveyed by the pump 26 via the first valve device 32. In the circuit 24 the second rotor 20 is connected in a fluidic manner parallel to the first rotor 14, whereby the rotors 14 and 22 can be supplied with the fluid pumped by the pump 26 via the first valve device 32.

The circuit 24 has a first flow path SP1 and a second flow pad SP2. The flow paths SP1 and SP2 are also referred to as flow branches. The stators 16 and 22 are arranged in the flow path SP1 such that the stators 16 and 22 in the first flow path SP1 are connected in parallel to one another in terms of flow. The rotors 14 and 20 are arranged in the second flow path SP2 such that the rotors 14 and 20 in the second flow path SP2 are connected in parallel to one another in terms of flow. The stators 16 and 22 thus form a stator pair, which is also referred to as a stator system. In addition, the rotors 14 and 20 form a rotor pair, which is also referred to as a rotor system.

In the first embodiment, it is provided that in the first switching state Z1 with respect to the flow paths SP1 and SP2, only the flow path SP1 is fluidically connected to the pump 26 via the valve device 32, while the flow path SP2 is fluidically separated from the pump 26 by means of the valve device 32. If the pump 26 thus delivers the fluid while the valve device 32 is in the first switching state Z1, the fluid delivered by the pump 26 and in particular delivered to the valve device 32 is introduced by the valve device 32 with respect to the flow paths SP1 and SP2 exclusively into the flow path SP1, so that with respect to the stator pair and the rotor pair, exclusively the stator pair and thus with respect to the stators 16 and 22 and the rotors 14 and 20, exclusively the stators 16 and 22 are supplied with the fluid delivered by the pump 26 via the valve device 32, while the rotor pair, thus the rotors 14 and 20, are not supplied with the fluid delivered by the pump 26 via the valve device 32.

In the first embodiment, it is provided that in the second switching state Z2 with respect to the flow paths SP1 and SP2, only the flow path SP2 is fluidically connected to the pump 26 via the valve device 32, while the flow path SP1 is fluidically separated from the pump 26 by means of the valve device 32. If the pump 26 thus delivers the fluid while the valve device 32 is in the second switching state Z2, the fluid delivered by the pump 26 and in particular delivered to the valve device 32 is introduced by the valve device 32 with respect to the flow paths SP1 and SP2 exclusively into the flow path SP2, so that with respect to the stator pair and the rotor pair, exclusively the rotor pair and thus with respect to the stators 16 and 22 and the rotors 14 and 20, exclusively the rotors 14 and 20 are supplied with the fluid delivered by the pump 26 via the valve device 32, while the stator pair, and thus the stators 16 and 22, are not supplied with the fluid delivered by the pump 26 via the valve device 32.

Also arranged in the circuit 24 is a reservoir 28 in which the fluid can be or is at least temporarily received. For example, the reservoir 28 is a tank or a reservoir also referred to as a coolant and/or lubricant reservoir. The pump 26 can, in particular by operating the pump 26, suck in the fluid from the reservoir 28 and thus convey it towards itself and in particular convey it through itself and in the process convey it to the cooling device 30 and convey it through the cooling device 30 and convey it via the cooling device 30 to the valve device 32 and, in particular in the first switching state Z1 and in the second switching state Z2, convey it through the valve device 32.

If the fluid, in particular the reservoir 28, is pumped by means of the pump 26 while the valve device 32 is in the first switching state Z1, a first volume flow Q_S formed by the fluid pumped by the pump 26 is guided into the flow path SP1 via the valve device 32. If the fluid, in particular the reservoir 28, is pumped by means of the pump 26 while the valve device 32 is in the second switching state Z2, a second volume flow Q_R formed by the fluid pumped by means of the pump 26 is subsequently guided into the flow path SP2 via the valve device 32. A first supply flow QS1 resulting from the first volume flow Q_S of the fluid and designed as a volume flow can be fed to the stator 16, which can thus be supplied or is supplied with the fluid forming the first supply flow QS1 and pumped by means of the pump 26. A second supply flow Q_R1 of the fluid, which results from the second volume flow Q_R of the fluid and is designed as a volume flow, can be fed to the rotor 14, so that the rotor 14 can be supplied or is supplied with the fluid forming the second supply flow Q_R1 and conveyed by means of the pump 26. If, for example, the reservoir 28 is conveyed by means of the pump 26, the fluid conveyed by means of the pump 26, in particular at least a part of the fluid conveyed by means of the pump 26, forms a machine flow Q_em designed as a volume flow, which flows to and through the cooling device 30 and to the valve device 32 and in particular in the respective gen switching state Z1, Z2 flows through the valve device 32. In the first switching state Z1, for example, the machine current Q_eM forms the first volume flow Q_S, in particular such that the machine current Q_eM corresponds to the first volume flow Q_S. In the second switching state Z2, for example, the machine current Q_eM forms the second volume flow Q_R, for example such that the machine current Q_eM corresponds to the second volume flow Q_R. The first volume flow Q_S is also referred to as the stator current, since the stators 16 and 22 can be cooled and/or lubricated by means of the stator current formed as a volume flow. The second volume flow Q_R is also referred to as the rotor current, since the rotors 14 and 22 can be cooled and/or lubricated by means of the rotor current formed as a volume flow of the fluid. In particular, for example, the fluid conveyed by means of the pump 26 forms a cooling flow Q_K in the form of a volume flow, which flows, for example, to the cooling device 30, in particular flows through the cooling device 30. For example, the cooling flow Q_K forms the machine flow Q_eM, so that, for example, the machine flow Q_eM results from the cooling flow Q_K. In particular, it is conceivable that the cooling flow Q_K corresponds to the machine flow Q_eM. It should be explicitly emphasized that the machine flow Q_eM, the cooling flow Q_K, the volume flows Q_S and Q_R and the supply flows Q_S1 and Q_R1 are not electrical currents, but volume flows of the fluid, i.e. volume flows formed by the fluid conveyed by means of the pump 26.

In the first embodiment, the electric drive device 10 has a second valve device 34 which is arranged in both the flow path SP1 and the flow path SP2, such that the second valve device 34 is arranged downstream of the first rotor 14, downstream of the first stator 16, upstream of the second rotor 20 and upstream of the second stator 22. In other words, the second valve device 34 is arranged in the first flow path SP downstream of the stator 16 and upstream of the stator 22, and the valve device 34 is arranged in the flow path SP2 downstream of the rotor 14 and upstream of the rotor 20.

The valve device 34 can be used to adjust the supply of the second rotor 20 and the second stator 22 with the coolant and/or lubricant conveyed by the pump 26 and thereby provided by the pump 26. It can be seen that the first flow path SP1 and thus the circuit 24 have a first supply line 36, which is thus part of the first flow path SP1. In addition, the second flow path SP2 and thus the circuit 24 have a second supply line 38, which is thus part of the second flow path SP2. The stator 22 can be supplied with the fluid via the supply line 36, and the rotor 20 can be supplied with the fluid via the supply line 38. The valve device 34 is arranged both in the supply line 36 and in the supply line 38. In the case of the 1 In the first embodiment shown, the second valve device 34 is designed as a control solenoid valve. The second valve device 24 can be switched to different intermediate switching states in addition to the supply state VZ and the blocking state SZ by controlling the second valve device 34, in particular electrically or electronically, whereby intermediate values of the fluid flow between zero and a maximum fluid flow can be set. The first valve device 32 is also designed as a control solenoid valve, but can also be designed as a solenoid valve, in particular for cost reasons, which has two switching positions, the supply state VZ and the blocking state SZ.

For example, the second valve device 34 has a second valve part which can be moved, for example, in particular relative to a second valve housing of the second valve device 34, between a supply position causing the supply state VZ and a blocking position causing the blocking state SZ, in particular translationally and/or rotationally. In particular, the second valve part can be moved between the blocking position and the supply position by controlling the second valve device 34, in particular electrically or electronically. In the supply state VZ, the fluid delivered by the pump 26 can flow through the second rotor 20 and the second stator 22 via the second valve device 34, such that in the supply state VZ of the valve device 34, the stator 22 is fluidically connected to the valve device 32 via the valve device 34. In addition, in the supply state VZ of the valve device 34, the second rotor 20 is fluidically connected to the valve device 32 via the valve device 34. In the blocking state SZ, a supply of the second rotor 20 and the second stator 22 with the fluid conveyed by means of the pump 26 via the second valve device 34 is prevented, in particular in such a way or in that in the blocking state SZ of the valve device 34, the stator 22 and the rotor 20 are fluidically separated from the valve device 32 by means of the valve device 34.

If the fluid is pumped by means of the pump 26, in particular from the reservoir 28, while the valve device 32 is in the switching state Z1 and the valve device 34 is in the supply state VZ, both the stator 16 and the stator 22 are supplied with the fluid conveyed by means of the pump 26, while the rotors 14 and 20 are not supplied with the fluid conveyed by means of the pump 26. In this case, for example, in particular at a first distribution point AS1, the first volume flow Q_S is divided into the first supply flow Q_S1 and a third supply flow Q_S2 designed as a volume flow of the fluid, wherein the third supply flow Q_S2 flows to the stator 22, in particular via the valve device 34, and is thus supplied to the stator 22, so that the stator 22 can be lubricated and/or cooled by means of the third supply flow Q_S2. If the fluid is pumped by means of the pump 26, in particular from the reservoir 28, while the valve device 32 is in the second switching state Z2 and the valve device 34 is in the supply state VZ, the second volume flow Q_R is divided, in particular at a second division point AS2, into the second supply flow Q_R1 and into a fourth supply flow Q_R2 designed as a volume flow. It can be seen that the fourth supply flow Q_R2 is fed to the second rotor 20, in particular via the valve device 34, so that the second rotor 20 is supplied with the fourth supply flow Q_R2 or can be supplied with it. In other words, the second rotor 20 can thus be lubricated and/or cooled by means of the fourth supply flow Q_R2. At this point, it should be explicitly noted that the third supply current Q_S2 and the fourth supply current Q_R2 are not electrical currents, but rather volume flows of the fluid, i.e. volume flows formed by the fluid conveyed by means of the pump 26.

If the pump 26 delivers the fluid while the valve device 32 is in the first switching state Z1 and the valve device 34 is in the blocking state SZ, the stator 16 is supplied with the fluid, in this case with the first supply current Q_S1, while the stator 22, the rotor 14 and the rotor 20 are not supplied with the fluid delivered by the pump 26. In this case, the supply current Q_S1 corresponds, for example, to the first volume flow Q_S. If, for example, the pump 26 delivers the fluid while the valve device 32 is in the second switching state Z2 and the valve device 34 is in the blocking state SZ, the rotor 14 is supplied with the supply current Q_R1 and thus with the fluid that forms the supply current Q_R1, while the rotor 20, the stator 16 and the stator 2 are not supplied with the fluid delivered by the pump 26. In this case, for example, the supply current Q_R1 corresponds to the second volume flow Q_R. If the valve device 32 is in the first switching state in the first switching state Z1 and the valve device 34 is in the supply state VZ, then, for example, the respective supply current Q_S1, Q_S2 is less than the volume flow Q_S, in particular such that the supply currents Q_S1 and Q_S2 add up to the volume flow Q_S. If the valve device 32 is in the second switching state Z2 and the valve device 34 is in the supply state VZ, then, for example, the respective supply current Q_R1, Q_R2 is less than the volume flow Q_R, in particular such that the supply currents Q_R1 and Q_R2 add up to the second volume flow Q_R. Furthermore, 1 It can be seen that the respective supply line 36, 38 is a branch leading from the stator 16 to the stator 22 or from the rotor 14 to the rotor 20 or at least a part of such a branch of the circuit 24 leading from the stator 16 to the stator 22 or from the rotor 14 to the rotor 20.

In the first embodiment, it is provided that the circuit 24 has a branching point VS, which in the first embodiment is arranged downstream of the pump 26 and upstream of the valve device 32, in particular upstream of the cooling device 30. Thus, in the first embodiment, the branching point VS is arranged upstream of the rotor pair and upstream of the stator pair. At the branching point VS, the coolant and/or lubricant conveyed by the pump 26 and thereby provided by the pump 26 can be divided into a first fluid flow of the fluid flowing as a volume flow through a supply branch VZZ of the circuit 24 and a second fluid flow of the fluid flowing as a volume flow through a consumer branch VBZ of the circuit 24 leading to at least one parallel consumer 40. In the present case, the first fluid flow is, for example, the cooling flow Q_K, and the second fluid flow is a consumer flow Q_pV designed as a volume flow. It should be explicitly emphasized that the first fluid flow, the second fluid flow, the cooling flow Q_K and the consumer flow Q_pV are not electrical currents, but volume flows of the fluid, thus volume flows formed by the fluid conveyed by means of the pump 26.

For example, the circuit 24 has a pump branch PZ common to the supply branch VZZ and the consumer branch VBZ, in which the pump 26 is arranged. At the branching point VS, the pump branch PZ branches into the supply branch VZZ and the consumer branch VBZ, with the cooling device 30 being arranged in the supply branch VZZ. Furthermore, the valve device 32 can be arranged in the supply branch VZZ. The supply branch VZZ is a path or branch common to the flow paths SP1 and SP2, for example such that the supply branch VZZ branches off into the flow paths SP1 and SP2, in particular via the valve device 32.

At least one parallel consumer 40 is arranged in the consumer branch VBZ, wherein it is conceivable that several parallel consumers, namely the parallel consumer 40 and at least one or more further parallel consumers, are arranged in the consumer branch VBZ. For example, the parallel consumer 40 is a transmission. The parallel consumer 40 can be part of the drive device 10.

In the consumer branch VBZ there is arranged a valve 42, for example designed as a solenoid valve, via which the parallel consumer 40 can be supplied with the fluid, that is to say with the consumer current Q_pV. The valve 42 can thus adjust a supply of the parallel consumer 40 with the fluid conveyed by means of the pump 26, in particular by controlling the valve 4, in particular electrically or electronically. For example, the valve 42 can be switched between a closed state SSZ and a released state FZ, in particular by controlling the valve 42, in particular electrically or electronically. In the released state FZ, the valve 42 releases the consumer branch VBZ, so that in the released state FZ, in particular, the parallel consumer 40 is fluidically connected to the pump 26 via the valve 42. As a result, in the released state FZ of the valve 42, the parallel consumer 40 can be supplied with the fluid conveyed by means of the pump 26 via the valve 42. If, for example, the valve device 32 is in the switching state Z1 or the switching state Z2 while the valve 42 is in the release state FZ, the fluid conveyed by means of the pump 26 is divided at the branching point VS into the cooling flow Q_K and the consumer flow Q_pV, thus into the first fluid flow and the second fluid flow, wherein the first fluid flow (cooling flow Q_K) flows to the cooling device 30 and to the valve device 32 and in particular subsequently flows through the valve device 32, wherein the second fluid flow (consumer flow Q_pV) flows through the consumer branch VBZ, flows to the valve 42, flows through the valve 42 and is finally fed to the parallel consumer 40. However, if, for example, the valve 42 is in the closed state SSZ while the pump 26 is conveying the fluid and the valve device 32 is in the switching state Z1 or the switching state Z2, the valve 42 blocks the consumer branch VBZ, so that the parallel consumer 40 is not supplied with the fluid conveyed by means of the pump 26, and so that, for example, the cooling flow Q_K and in particular the machine flow Q_M correspond to the, in particular entire, fluid conveyed by means of the pump 26, thus a conveying volume flow designed as a volume flow, which is conveyed by means of the pump 26, thus is formed by the fluid conveyed by means of the pump 26. If the valve 42 is in the release state FZ while the valve device 32 is in the switching state Z1 or the switching state Z2, then, as previously described with reference to the fluid conveyed by means of the pump 26, the delivery flow designed as a volume flow is divided into the consumer flow Q_pV and the cooling flow Q_K, in particular at the branching point VS.

In the third switching state Z3 of the valve device 32 according to the second embodiment V2, which is designed as a separation state or referred to as a separation state, a volume flow of the fluid from the pump 26 to the electrical machines 12 and 18, and thus a supply of the electrical machines 12 and 18 with the fluid conveyed by the pump 26, and thus with the delivery flow, is prevented by means of the first valve device 32, in that in the switching state Z3 the electrical machines 12 and 18 are fluidically separated from the pump 26, and in this case also from the valve device 32, by means of the valve device 32. In the present case, this is implemented in such a way that in the third switching state Z3 both the flow path SP1 and the flow path SP2 are fluidically separated from the pump 26, and in this case from the supply branch VZZ, by means of the valve device 32. If, for example, the valve device 32 is in the third switching state Z3, while the valve 42 is in the release state FZ and the pump 26 is pumping the fluid, the fluid pumped by the pump 26, in particular the entire delivery flow, flows at the branching point VS into the consumer branch VBZ. In other words, the consumer flow Q_pV then corresponds to the delivery flow, for example.

It can be seen that the respective electrical machine 12, 18 is connected in parallel to the parallel consumer 40 in terms of flow. If, for example, the electrical machines 12 and 18 are connected to the pump 26 with further consumers connected in parallel, a three-way valve can be advantageous in order to be able to advantageously supply the consumers and the electrical machines 12 and 18 with the fluid, and thus to be able to advantageously adjust, in particular regulate or control, a volume flow of the fluid conveyed by means of the pump 26. In particular, the flow rate can thus be adjusted to different partial volumes as required. flow rates such as the cooling flow Q_K or the machine flow Q_eM, the consumer flow Q_pV and at least one other consumer flow. The flow rate to be conveyed or conveyed by means of the pump 26, thus formed by the fluid conveyed by means of the pump 26, is divided into 1 denoted by Q_F.

2 shows a schematic representation of a second embodiment of the electric drive device 10. In the second embodiment, the second valve device 34 is designed to set a plurality of values of the respective supply current Q_S2, Q_R2 that are different from zero and from one another and in particular greater than zero. For this purpose, for example, the second valve device 34 can be switched to the supply state VZ and to a further or preferably to a plurality of further supply states, wherein one of the values of the respective supply current Q_S2, Q_R2 is set in the respective supply state. If, for example, the valve device 32 is in the first switching state Z1 while the pump 26 is pumping the fluid, the values of the supply current Q_S2 that are different from one another and from zero can be set by setting the different supply states of the second valve device 34. If the valve device 32 is in the second switching state Z2 while the pump 26 is pumping the fluid, the multiple values of the supply current Q_R2 that are different from one another and from zero and, in particular, greater than zero can be set by setting the supply states of the valve device 34 that are different from one another.

In the present case, it can be seen that a first throttle D1 is arranged in the flow path SP1 upstream of the valve device 34 and upstream of the valve device 32, and a second throttle D2 is arranged in the flow path SP2 upstream of the valve device 34 and upstream of the valve device 32.

Furthermore, in the second embodiment, it is provided that the second valve device 34 is designed as a hydraulically actuated or hydraulically actuated valve device, whereby the respective supply current Q_S2, Q_R2, i.e. the respective value of the respective supply current Q_S2 and Q_R2, is dependent on a pressure that prevails in the supply line 36 of the circuit 24, also referred to as a branch or designed as a branch of the circuit 24, leading from the first stator 16 to the second valve device 34, downstream of the first stator 16 and in this case upstream of the valve device 34, in particular upstream of the throttle D1. This means that by means of an actuating line BL, the pressure, in particular of the fluid, prevailing in the supply line 36 downstream of the stator 16 and upstream of the valve device 34, in particular upstream of the throttle D1, can be tapped or branched off from the supply line 36 and fed to the valve device 34, in particular to the second valve part of the valve device 34, in particular in such a way that the second valve part of the valve device 34 can be subjected to the pressure, in particular directly. Depending on the pressure, that is to say depending on the pressure values of the pressure, the second valve part can be moved into different supply positions, in particular relative to the second valve housing, wherein, in particular precisely, a respective one of the different supply positions, in particular precisely, brings about a respective one of the different supply states and thus, in particular precisely, a respective one of the different values of the respective supply current Q_R2, Q_S2 that are different from one another, different from zero and in particular greater than zero. Thus, the electrical machine 18 is supplied with the fluid in a pressure-dependent manner.

3 shows a schematic view of a third embodiment of the cooling system of an electric drive device 10. In the third embodiment, the second valve device 34 is not provided. Instead of the second valve device 34, a valve element 44, also referred to as a valve device, is arranged in the circuit 24 downstream of the first rotor 14 and downstream of the first stator 16, which is or can be fluidically connected to both the supply line 36 and the supply line 38. By means of the valve element 44, the supply lines 36 and 38 can be fluidically connected to the reservoir 28 or fluidically separated from the reservoir 28. For this purpose, the valve element 44 can be switched between a discharge state A, also referred to as a connection state, and a decoupling state B, in particular by controlling the valve element 44, in particular electrically or electronically. For example, the valve element 44 has a third valve part which can be moved, in particular translationally and/or translationally, between a discharge position causing the discharge state A and a decoupling position causing the decoupling state B by controlling the valve element 44, in particular relative to the third valve housing of the valve element 44. In the discharge state A, the supply lines 36 and 38 are fluidically connected to the reservoir 28 via the valve element 44, in particular at a respective coupling point arranged upstream of the rotor 20 or the stator 22 and downstream of the first valve device 32, so that, for example, at the respective coupling point at least a portion of the fluid of the supply line 36, 38 can be discharged and fed to the valve element 44 and introduced into the reservoir 28 via the valve element 44. In the decoupling state B, the supply lines 36 and 38 are fluidically separated from the reservoir 28 by means of the valve element 44 at the respective coupling point, so that no fluid is branched off from the respective supply line 36, 38 at the respective connection point.

Next shows 4 in a schematic representation, a fourth embodiment of the cooling circuit of an electric drive device 10. In the fourth embodiment, the circuit 24 has a first supply branch ZZ1 assigned to the first rotor 14, via which the fluid conveyed by means of the pump 26 can be fed to the first rotor 14 in order to supply the first rotor 14 with the fluid conveyed by means of the pump 26. The circuit 24 also has a second supply branch ZZ2 assigned to the second rotor 20 and connected in fluid terms parallel to the first supply branch ZZ1, via which the fluid conveyed by means of the pump 26 can be fed to the second rotor 20 in order to supply the second rotor 20. It can be seen that, for example, the second supply branch ZZ2 is part of the supply line 38. It is also conceivable that the first supply branch ZZ1 is part of the supply line 38. The supply branch ZZ1 can be flowed through, for example, by the supply current Q_R1, so that the supply current Q_R1 can be fed to the rotor 14 via the supply branch ZZ1. The supply branch ZZ2 can be flowed through, for example, by the supply current Q_R2, so that the supply current Q_R2 can be fed to the second rotor 20 via the supply branch ZZ2.

Out of 4 it can be seen that in the fourth embodiment neither the second valve device 34 nor the valve element 44 is provided. In the first supply branch ZZ1, a first check valve device 46 is arranged, which is connected in terms of flow parallel to the second rotor 20 and parallel to the second supply branch ZZ2, by means of which a backflow of the fluid away from the first rotor 14 can be prevented and a pressure-dependent switching on of the rotor cooling can be implemented particularly advantageously. The first check valve device 46 allows the supply flow Q_R1 to flow to the rotor 14. This means that the first check valve device 46 can be flowed through by the supply flow Q_R1 flowing to the rotor 14. In other words, the check valve device 46 automatically opens in the direction of the rotor 14 and blocks or closes in an opposite direction away from the rotor 14, and thus cannot be flowed through by the fluid in a direction away from the rotor 14. In the second supply branch ZZ2, a second check valve device 48 is assigned, which is connected in a fluidic manner parallel to the first rotor 14, in a fluidic manner parallel to the first supply branch ZZ1, and in a fluidic manner parallel to the first check valve device 46, by means of which a backflow of the fluid away from the second rotor 20 can be prevented. The second check valve device 48 can be flowed through in a direction toward the rotor 20 and thus by the supply flow Q_R2, so that the supply flow Q_R2 can be supplied to the second rotor 20 via the check valve device 48. However, the check valve device 48 cannot be flowed through by the fluid in a direction pointing away from the second rotor 20. It is provided that the check valve device 48 opens automatically in the direction of the rotor 20 and thus allows the supply current Q_R2 to flow towards the rotor 20, but the check valve device 48 automatically closes in an opposite direction pointing away from the rotor 20 and thus the fluid cannot flow through in the direction pointing away from the rotor 20.

In the first embodiment, the branching point VS is arranged downstream of the pump 26 and upstream of the cooling device 30. In the second embodiment, the branching point VS is also arranged downstream of the pump 26 and upstream of the cooling device 30. In the third embodiment, the branching point VS is also arranged downstream of the pump 26 and upstream of the cooling device. It is advantageous if the branching point VS, at which the consumer branch VBZ branches off from the flow part SP2 to supply the consumer 40, is arranged upstream of the cooling device 30, a coolant and lubricant in the consumer branch VBZ is uncooled and thus comparatively warmer, whereby a better lubricating effect for the consumer 40 can be achieved. In the fourth embodiment, however, the branching point VS is downstream of the pump 26, downstream of the cooling device 30 and downstream of the first valve device 32 and upstream of the first rotor 14 and the second rotor 20 and in particular in the flow part SP2, so that the consumer branch VBZ branches off from the second flow part SP2 at the branching point VS. Advantageously, in the fourth embodiment of the invention, lubricant management is less complex, since cooled coolant and lubricant reaches the consumer 40, so that a continuous increase in lubricant temperature at high loads, especially when the consumer 40 is a transmission, can be avoided, and so monitoring of a lubricant temperature in the reservoir 28 can be dispensed with. If the fluid is thus conveyed by means of the pump 26, in particular from the reservoir 28, so that the fluid forms the delivery flow Q_F conveyed by means of the pump 26 and flowing through the pump 26, and the valve device 32 is in the second switching state Z2, the supply flow Q_F also flows through the cooling device 30 and through the valve device 32, so that in the fourth embodiment the delivery flow Q_F corresponds, for example, to the cooling flow Q_K or forms the cooling flow Q_K. If the valve 42 is also in the release state FZ, the flow rate Q_F is divided at the branching point VS into the consumer flow Q_PV flowing through the consumer branch VBZ and into the machine flow Q_EM, in particular such that the consumer flow Q_PV and the machine flow Q_EM are each smaller than the flow rate Q_F, in particular such that the consumer flow Q_PV and the machine flow Q_EM add up to the flow rate Q_F. The machine flow Q_EM forms the second volume flow Q_R, in particular such that the machine flow Q_EM is the second volume flow Q_R or corresponds to the second volume flow Q_R. As already described above, in the flow path SP2, the second volume flow Q_R is divided into the second supply flow Q_R1 and the fourth supply flow Q_R2, wherein the second supply flow Q_R1 is fed to the rotor 14 via the feed branch ZZ1 and the check valve device 46 and the fourth supply flow Q_R2 is fed to the second rotor 20 via the feed branch ZZ2 and the check valve device 48. If the valve device 32 is in the first switching state Z1 while the pump 26 is feeding the fluid and the valve 42 is in the blocking state SSZ, for example the delivery flow Q_F is not divided at the branching point VS, but rather the delivery flow Q_F forms the machine flow Q_EM, in particular such that the delivery flow Q_F corresponds to the machine flow Q_EM, or that the delivery flow Q_F is the machine flow Q_EM, or vice versa. It can thus be seen that the machine flow Q_EM is a volume flow which, depending on the switching state Z1, Z2 of the valve device 32, is optionally supplied to the flow path SP1 or the flow path SP2 and is thus used to at least partially lubricate and/or cool the respective electrical machine 12, 18.

In summary, 1 stated the following: As 1 As can be seen, for example, the cooling flow Q_K and thus the machine flow Q_EM is initially fed to the electric machine 12. In particular, the electric machine 12 is an electric machine whose cooling and/or lubrication is of greater importance than that of another, second electric machine 18, so that, for example, a so-called master-slave concept is implemented, particularly with regard to the electric machines 12 and 18. The cooling flow Q_K or the machine flow Q_EM can be provided as needed, so that, for example, in particular by operating the pump 26, several volume flow values of the cooling flow Q_K or the machine flow Q_EM that are different from one another and different from zero, in particular closer to zero, can be set. This can be implemented, in particular, by adjusting the speed, that is, by varying a speed of the pump 26, in particular of the conveying element 27. By means of the upstream valve device 32, which in this case is designed as a 3/2-way valve and functions as a volume flow divider or is designed as a volume flow divider, a variable distribution of the cooling flow Q_K or machine flow Q_EM between the first stator 16 and the first rotor 14 is possible. In combination with the variable or variable, and therefore adjustable, cooling flow Q_K, the valve device 32 enables, for example, operating point-dependent cooling and/or lubrication of components to be cooled, such as in particular the electrical machines 12 and 18.

By opening a valve connected in parallel, for example designed as a 4/2-way valve and/or by opening the valve device 34 designed, for example, as a 4/2-way valve and connected in parallel or series, for example, thus for example by switching the valve device 34 to the supply state VZ, the respective volume flow Q_R, Q_S is divided, in particular depending on resistances in the respective hydraulic flow path SP1, SP2, into the supply flows Q_S1 and Q_S2 or Q_R1 and Q_R2.

Particularly good 1 it can be seen that the pump 26 has a suction connection 50 arranged in the reservoir 28, via which the pump 26 can suck in the fluid from the reservoir 28 and convey it to itself, in particular by operating the pump 26. The first stator 16 has a return connection 52, and the rotor 14 has a return connection 54. The stator 22 has a return connection 54, and the rotor 20 has a return connection 58. The fluid can flow off or away from the stator 16, the rotor 14, the stator 22 or the rotor 20 via the respective return connection 52, 54, 56, 58 and flow into the reservoir 28. so that a respective return connection 52, 54, 56, 58 is provided for a return of the fluid into the reservoir 28.

For example, by using additional and specifically provided resistors such as orifices and/or chokes, for example in front of assemblies such as the rotor 20 and the stator 22 of the second electrical machine 18, the respective volume flow Q_S, Q_R can be divided in such a way that, for example, the first electrical machine 12, i.e. its rotor 14 or stator 16, is supplied with the fluid with priority over the electrical machine 18, in particular over the rotor 20 or the stator 22, and is thus cooled and/or lubricated.

It can be seen that the at least one parallel consumer 40 is connected in parallel to the respective flow path SP1, SP2 as an additional consumer. It is conceivable that the parallel consumer 40, the valve 42 and the consumer branch VBZ are omitted. However, if the parallel consumer 40 and thus, for example, the valve 42 and the consumer branch VBZ are provided, the second embodiment V2 of the valve device 32 is advantageously used. The second embodiment V2 is also used in particular when a non-variable speed pump, i.e. a pump with a constant speed, is operated instead of the variable speed pump 26. In particular, the second embodiment V2 can ensure an advantageous and needs-based supply of the parallel consumer 40 with the fluid.

In the first embodiment, two valves in the form of valve devices 32 and 34 are used. In this case, it is preferably provided that the valve device 34 is an external component with respect to the valve device 32 and is thus arranged outside the valve device 32. Accordingly, it is preferably provided that the valve device 32 is an external component with respect to the valve device 34 and is thus arranged outside the valve device 34. The respective valve device 32, 34 can, as described, adjust, in particular control or regulate the respective volume flow of the fluid. In particular in the case of an increasing cooling and/or lubrication requirement from or to the second electrical machine 18 and/or with increasing requirements from or to the first electrical machine 12, a pressure-dependent switching on of or for the second electrical machine 18 can be advantageous. In this case, for example, a valve designed as a solenoid valve, for example, can only be provided or required for the first electrical machine 12, which is the case in the second embodiment in particular in the form of the valve device 32. For example, the valve device 32 is designed as a solenoid valve, wherein in the second embodiment the valve device 34, as previously described, is a hydraulically actuated or hydraulically actuable valve, such that the second valve part is not movable by means of electrical energy, but hydraulically or by means of the fluid. In contrast, the first valve device 32 or the first valve part is movable by means of electrical energy, for example, and therefore electrically.

Finally, 5 in a schematic representation, a fifth embodiment of an electric drive device 10. The fifth embodiment of the cooling circuit corresponds to the fourth embodiment of the cooling circuit, but additionally has a hydraulic valve 43 and an orifice 45 arranged downstream of the hydraulic valve 43. The valve 43 is provided upstream of the parallel consumer 40 in the consumer branch VBZ and has a valve piston, wherein on the one hand a first pressure force from a first control pressure 43b derived downstream of the hydraulic valve 43 and upstream of the orifice 45 and on the other hand a spring force act on the valve piston, wherein an effective direction of the spring force is opposite to an effective direction of the first pressure force. In addition, a second pressure force from a second control pressure derived upstream of the hydraulic valve 43 and downstream of the orifice 45 acts on the valve piston, wherein an effective direction of the second pressure force is the same as the effective direction of the spring force. As an alternative to the first valve device 32 in the first embodiment V1, it can be advantageous, particularly in the fifth embodiment of the electric drive device 10, to provide a third embodiment V3 of the valve device 32. The valve device 32 of the third embodiment V3 is designed such that it can be switched between the first switching state Z1, in which only the stators 16, 22 are supplied with coolant and lubricant, and an alternative second switching state Z2A, in which both the stators 16, 22 and the rotors 14, 20 as well as the parallel consumer 40 are supplied with coolant and lubricant.

A design of the cooling circuit of the fifth embodiment of an electric drive device 10 is advantageously carried out in a first step without the hydraulic valve 43 on the basis of the path resistance of the second flow path SP2, in which the rotors 14, 20 are arranged, on the one hand, and on the basis of the path resistance of the consumer branch VBZ, in which the parallel consumer 40 is arranged, on the other hand. In a second step, the valve 43 is designed so that the valve 43 closes under defined boundary conditions that ensure a maximum pressure difference across the hydraulic valve 43, for example a maximum volume flow at a minimum prevailing temperature. In other words, the design of the valve 43 based on the boundary conditions determined in the first step means that the valve 43 reacts and closes under conditions that lead to a higher pressure difference across the orifice 45. This reduces or prevents an oversupply of the parallel consumer with coolant and lubricant.

list of reference symbols

10

electric drive device

12

first electric machine

14

first rotor

16

first stator

18

second electric machine

20

second rotor

22

second stator

24

circulation

26

pump

27

conveyor element

28

reservoir

29

Motor

30

cooling device

32

first valve device

34

second valve device

36

supply line

38

supply line

40

parallel consumers

42

valve

43

valve

43b

First tax pressure

43a

Second control pressure

44

valve element

45

aperture

46

check valve device

48

check valve device

50

suction connection

52

return connection

54

return connection

56

return connection

58

return connection

SP1

flow path

SP2

flow path

ZZ1

feed branch

ZZ2

feed branch

Q_S1

supply current

Q_S2

supply current

Q_R1

supply current

Q_R2

supply current

Q_S

volume flow

Q_R

volume flow

A

purgative state

B

decoupling state

AS1

distribution point

AS2

distribution point

VZ

supply status

SZ

locked state

Z1

first switching state

Z2

Second switching state

Z2A

Alternative second switching state

Z3

Third switching state

V1

First version

V2

Second embodiment

V3

Third embodiment

FZ

release state

SSZ

closed state

VS

branch point

Q_K

cooling current

VZZ

supply branch

Q_pV

consumer flow

VBZ

consumer sector

Q_eM

machine current

Q_F

flow rate

PZ

pump branch

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was 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 accepts no liability for any errors or omissions.

Cited patent literature

• DE 11 2015 007 075 T5 [0002]

Claims (14)

Electric drive device (10) for a motor vehicle, with a first electric machine (12) which has a first rotor (14) and a first stator (16), with a second electric machine (18) which has a second rotor (20) and a second stator (22), with a circuit (24) common to the electric machines (12, 18) through which a coolant and/or lubricant can flow, in which the electric machines (12, 18) are arranged, which are to be cooled and/or lubricated by means of the coolant and/or lubricant, with a pump (26) arranged in the circuit (24) by means of which the coolant and/or lubricant can be conveyed through the circuit (24), with a cooling device (30) arranged in the circuit (24) downstream of the pump (26) for cooling the coolant and/or lubricant, and with a circuit (24) downstream of the cooling device (30) and a first valve device (32) arranged upstream of the electrical machines (12, 18), by means of which a supply of the electrical machines (12, 18) with the coolant and/or lubricant conveyed by means of the pump (26) and thereby provided by the pump (26) can be adjusted, characterized in that: - in the circuit (24), the second stator (22) is connected in parallel to the first stator (16), which can be supplied with the coolant and/or lubricant conveyed by means of the pump (26) via the first valve device (32); and - in the circuit (24), the second rotor (20) is connected in parallel to the first rotor (14), which can be supplied with the coolant and/or lubricant conveyed by means of the pump (26) via the first valve device (32). Electric drive device (10) according to claim 1 , characterized in that a second valve device (34) is arranged in the circuit (24) downstream of the first rotor (14), downstream of the first stator (16), upstream of the second rotor (20) and upstream of the second stator (22), by means of which a supply of the second rotor (20) and the second stator (22) with the coolant and/or lubricant conveyed by means of the pump (26) and thereby provided by the pump (26) can be adjusted. Electric drive device (10) according to claim 2 , characterized in that the second valve device (34) can be switched between: - a supply state (VZ), in which the second rotor (20) and/or the second stator (22) can be supplied with the coolant and/or lubricant conveyed by means of the pump (26) via the second valve device (34); and - a blocking state (SZ), in which a supply of the second rotor (20) and the second stator (22) with the coolant and/or lubricant conveyed by means of the pump (26) via the second valve device (34) is prevented. Electric drive device (10) according to claim 2 or 3 , characterized in that the second valve device (34) is designed to set a plurality of values, different from zero, of a respective fluid flow (Q_R2, Q_S2) of the coolant and/or lubricant to be supplied to the second rotor (20) and/or the second stator (22) via the second valve device (34) and formed by the coolant and/or lubricant conveyed by means of the pump (26). Electric drive device (10) according to claim 4 , characterized in that the second valve device (34) is designed as a hydraulically actuable valve device, whereby the fluid flow (Q_R2, Q_S2) is dependent on a pressure prevailing in a branch (36) of the circuit (24) leading from the first stator (16) to the second valve device (36) downstream of the first stator (16). Electric drive device (10) according to one of the preceding claims, characterized in that: - the circuit (24) has a first supply branch (ZZ1) assigned to the first rotor (14), via which the coolant and/or lubricant delivered by the pump (26) can be fed to the first rotor (14) in order to supply the first rotor (14) with the coolant and/or lubricant delivered by the pump (26); - the circuit (24) has a second supply branch (ZZ2) assigned to the second rotor (20) and connected in parallel to the first supply branch (ZZ1), via which the coolant and/or lubricant delivered by the pump (26) can be fed to the second rotor (20) in order to supply the second rotor (20) with the coolant and/or lubricant delivered by the pump (26); - in the first supply branch (ZZ1) there is arranged a first non-return valve device (46) which is connected parallel to the second rotor (20) and parallel to the second supply branch (ZZ2), by means of which a backflow of the coolant and/or lubricant away from the first rotor (14) can be prevented; and - in the second supply branch (ZZ2) there is arranged a second non-return valve device (48) which is connected parallel to the first rotor (14), parallel to the first supply branch (ZZ1) and parallel to the first non-return valve device (46), by means of which a backflow of the coolant and/or lubricant away from the second rotor (20) can be prevented. Electric drive device (10) according to one of the preceding claims, characterized in that the circuit (24) has a branching point (VS) downstream of the pump (26), upstream of at least one of the rotors (14, 20) and upstream of at least one of the stators (16, 22), at which the coolant and/or lubricant conveyed by means of the pump (26) and thereby provided by the pump (26) flows into a first fluid flow of the coolant and/or lubricant flowing into a supply branch (38, VZZ) of the circuit (24), via whose supply branch (38, VZZ) the at least one rotor (14, 20) and the at least one stator (16, 22) connected in parallel to the at least one rotor (14, 20) can be supplied with the coolant and/or lubricant conveyed by means of the pump (26), and a consumer branch leading to at least one parallel consumer (40). (VBZ) of the circuit (24) flowing, second fluid stream of the coolant and/or lubricant can be divided. Electric drive device (10) according to claim 7 , characterized in that the branching point (VS) is arranged downstream of the first valve device (32), upstream of the at least one rotor (14, 20) and upstream of the at least one stator (16, 22) in the circuit (24). Electric drive device (10) according to claim 7 , characterized in that the branching point (VS) is arranged downstream of the pump (26) and upstream of the cooling device (30). Electric drive device (10) according to one of the preceding claims, characterized by a reservoir (28) for at least temporarily holding the coolant and/or lubricant. Electric drive device (10) according to claim 9 , characterized in that: - the circuit (24) has a first supply line (36) assigned to the second stator (22), via which the coolant and/or lubricant pumped by means of the pump (26) can be fed to the second stator (22) in order to supply the second stator (22) with the coolant and/or lubricant pumped by means of the pump (26); - the circuit (24) has a second supply line (38) assigned to the second rotor (20), via which the coolant and/or lubricant pumped by means of the pump (26) can be fed to the second rotor (20) in order to supply the second rotor (20) with the coolant and/or lubricant pumped by means of the pump (26); and - a valve element (44) is arranged in the circuit (24) downstream of the first rotor (14) and downstream of the first stator (16), by means of which the supply lines (36, 38) can be optionally fluidically connected to the reservoir (28) or fluidically separated from the reservoir (28). Electric drive device (10) according to claim 9 or 10 , characterized in that the pump (26) has a suction connection (50) arranged in the reservoir (28), wherein the first stator (16) and the first rotor (14) each have a return connection (52, 54) for a return of the coolant and/or lubricant into the reservoir (28). Electric drive device (10) according to one of the preceding claims, characterized in that the first valve device (32) can be switched to a separation state (Z3) in which the electrical machines (12, 18) are fluidically separated from the pump (26) by means of the first valve device (32), whereby in the separation state (Z3) a volume flow of the coolant and/or lubricant from the pump (26) to the electrical machines (12, 18) is prevented. Electric drive device (10) according to one of the preceding claims, characterized in that a hydraulic valve (43) and an orifice (45) are provided in the consumer branch (VBZ) of the circuit (24) leading to the at least one parallel consumer (40) upstream of the parallel consumer (40), wherein the hydraulic valve (43) has a valve piston on which a first pressure force from a first control pressure (43b) derived downstream of the hydraulic valve (43) and upstream of the orifice (45) and a spring force act on the other hand, wherein an effective direction of the spring force is opposite to an effective direction of the first pressure force, and wherein a second pressure force from a second control pressure (43a) derived downstream of the hydraulic valve (43) and downstream of the orifice (45) acts on the valve piston, wherein an effective direction of the second pressure force is the same as the effective direction of the spring force.

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