Electric drive device for a motor vehicle, motor vehicle and method for operating such an electric drive device

Abstract

The invention relates to an electric drive device (10) for a motor vehicle, comprising at least one electric machine (12) by means of which the motor vehicle can be driven, comprising a first circuit (20) through which a lubricant and / or coolant can flow as the first fluid, a second circuit (24) through which a cooling fluid different from the first fluid can flow as the second fluid, and a first heat exchanger (26) arranged both in the first circuit (20) and in the second circuit (24), via which heat can be exchanged between the first fluid and the second fluid. A refrigerant circuit (28) is provided as the third circuit, through which a refrigerant different from the first fluid and the second fluid can flow as the third fluid.A second heat exchanger (30) is provided, which is arranged in both the first circuit (20) and the third circuit (28), via which heat can be exchanged between the first fluid and the third fluid.

Description

[0001] The invention relates to an electric drive device for a motor vehicle, in particular for a car, according to claim 1. Furthermore, the invention relates to a motor vehicle with such an electric drive device. The invention also relates to a method for operating such an electric drive device.

[0002] The CN 103 65 770 A is known to be a thermal management system for an electric vehicle with range extender, which has a battery temperature control system, a cooling circuit system for other components and an air conditioning circuit system.

[0003] JP 2011-218936 A discloses a vehicle cooling device in which high-temperature oil escaping from a transmission is conveyed via an oil line to a line between an evaporator and a compressor of an air conditioning system. A further line, which is part of the oil line, runs along the line. This results in heat exchange between the oil flowing through the further line and the refrigerant of the air conditioning system flowing through the line.

[0004] JP 2014 - 110 705 A discloses a cooling device for a rotating electrical machine, which is branched into a first branch channel for supplying coolant to a coil side and a second branch channel for supplying the coolant to a permanent magnet side of the electrical machine.

[0005] DE 10 2018 211 568 A1 discloses a refrigeration system for a motor vehicle.

[0006] DE 10 2022 101 131 A1 discloses an electric motor drive unit for a motor vehicle.

[0007] The object of the present invention is to provide an electric drive device for a motor vehicle, a motor vehicle with such an electric drive device and a method for operating such an electric drive device, so that a particularly energy-efficient operation of the motor vehicle can be realized.

[0008] This object is achieved by an electric drive device having the features of patent claim 1, by a motor vehicle having the features of patent claim 9, and by a method having the features of patent claim 10. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

[0009] A first aspect of the invention relates to an electric drive device, also referred to as an electric drive unit or electromotive drive unit, for a motor vehicle, also simply referred to as a vehicle, whose interior, also referred to as a passenger cell, passenger compartment or cabin, is formed by a structure of the motor vehicle, designed, for example, as a self-supporting body. The motor vehicle, preferably designed as a motor vehicle, in particular as a passenger car, has the electric drive device in its fully manufactured state and can be driven, in particular purely electrically, by means of the electric drive device. The electric drive device has at least one or exactly one electric machine, by means of which the motor vehicle can be driven, in particular purely electrically.Preferably, the electrical machine, which is also referred to as drive machine or electric drive machine, is a high-voltage component whose electrical voltage, in particular electrical operating or nominal voltage, is preferably greater than 50 volts, in particular greater than 60 volts, and very preferably amounts to several hundred volts.

[0010] The electric drive device has a first circuit, also referred to as the first circuit. A lubricant and / or coolant can flow through the first circuit, wherein the lubricant and / or coolant is a first fluid, thus also referred to as the first fluid. Preferably, the lubricant and / or coolant is a liquid. Preferably, the lubricant and / or coolant (fluid) is an oil, so that, for example, the first circuit is also referred to as an oil circuit or is designed as an oil circuit.

[0011] The electric drive device also has a second circuit, also simply referred to as a second circuit, which is preferably at least partially, in particular completely, fluidically separated from the first circuit. A cooling fluid different from the first fluid can flow through the second circuit. The cooling fluid is a second fluid. In other words, the cooling fluid is also referred to as a second fluid. The cooling fluid is preferably a liquid. For example, the cooling fluid is or comprises water, in particular at least partially, so that the cooling fluid is also referred to, for example, as cooling water. The second circuit is also referred to as a cooling circuit or vehicle cooling circuit.

[0012] The electric drive device also has a first heat exchanger, which is arranged in both the first circuit and the second circuit and can therefore be flowed through by both the first fluid and the second fluid. Heat can be exchanged between the first fluid and the second fluid via the first heat exchanger. If, for example, the first fluid has a higher temperature than the second fluid on its way through the first heat exchanger, heat is transferred from the first fluid to the second fluid via the first heat exchanger, as a result of which the first fluid is cooled and the second fluid is heated. If, for example, the second fluid has a higher temperature than the first fluid on its way through the first heat exchanger, heat is transferred from the second fluid to the first fluid via the first heat exchanger, as a result of which the second fluid is cooled and the first fluid is heated.Preferably, the first fluid and the second fluid are components of the electric drive device.

[0013] In order to be able to realize particularly energy-efficient operation of the electric drive device and thus of the motor vehicle, a third circuit, also referred to as a third circuit, is provided according to the invention, which is preferably at least partially, in particular completely, separated from the first circuit. The third circuit is preferably at least partially, in particular completely, separated from the second circuit. A coolant that is different from the first fluid and the second fluid can flow through the third circuit. The coolant is a third fluid. In other words, the coolant is also referred to as a third fluid. The third circuit is thus a coolant circuit of the electric drive device. The third fluid is preferably a component of the electric drive device.

[0014] Furthermore, the invention provides for a second heat exchanger, in particular provided in addition to the first heat exchanger, to be arranged both in the first circuit and in the third circuit, such that heat can be exchanged between the first fluid and the third fluid via the second heat exchanger. Both the first fluid and the third fluid can therefore flow through the second heat exchanger. If, for example, the first fluid has a higher temperature than the third fluid on its way through the second heat exchanger, heat is transferred from the first fluid to the third fluid via the second heat exchanger, thereby cooling the first fluid and heating the third fluid.If, for example, the third fluid has a higher temperature than the first fluid on its way through the second heat exchanger, heat is transferred from the third fluid to the first fluid via the second heat exchanger, whereby the first fluid is heated and the third fluid is cooled. Preferably, the second heat exchanger is arranged outside the first heat exchanger, which is preferably arranged outside the second heat exchanger. Preferably, the heat exchangers are spaced apart from one another, in particular completely. With the invention, heat can advantageously be exchanged between the first fluid and the second fluid as well as between the first fluid and the third fluid, without undesirable, excessive heat losses occurring, as is the case, for example, with conventional solutions.

[0015] For example, the interior space can be heated using the third fluid. For this purpose, a third heat exchanger, provided in particular in addition to the first heat exchanger and in addition to the second heat exchanger, is arranged in the third circuit, for example, through which third fluid can flow and around which air to be supplied to the interior space, i.e. air to be introduced into the interior, can flow. For example, the third heat exchanger is arranged outside the first heat exchanger and outside the second heat exchanger, with the first heat exchanger preferably being arranged outside the third heat exchanger and the second heat exchanger preferably being arranged outside the third heat exchanger. The first heat exchanger, the second heat exchanger, and the third heat exchanger are preferably completely spaced from one another in pairs.For example, heat can be exchanged between the air (also referred to as cabin air) and the third fluid via the third heat exchanger, in particular such that heat is transferred from the third fluid to the cabin air via the third heat exchanger. This heats the cabin air. The cabin air is introduced into the interior, which allows the interior to be heated. The invention enables particularly energy-efficient heating of the cabin air and thus the interior, since undesirable excessive heat losses can be avoided compared to conventional solutions.As a result, the amount of electrical energy required to heat the interior can be kept particularly low, so that, for example, a particularly long electrical range of the motor vehicle, which is preferably designed as a hybrid vehicle or as an electric vehicle, in particular as a battery-electric vehicle (BEV), can be achieved.

[0016] Since the first heat exchanger is arranged in both the first circuit and the second circuit, the first circuit and the second circuit are thermally coupled to one another via the first heat exchanger, i.e., by means of the first heat exchanger. Since the second heat exchanger is arranged in both the first circuit and the third circuit, the first circuit and the third circuit are thermally coupled to one another via the second heat exchanger, i.e., by means of the second heat exchanger. This prevents an excessive amount of heat from being lost unused compared to conventional solutions. In the invention, this heat, which is lost unused in conventional solutions, can be used to warm, i.e., heat, the interior, in particular via the third fluid.

[0017] The invention is based in particular on the following findings and considerations: Typically, vehicles designed as electric vehicles, for example, have the problem that their range is significantly reduced in cold ambient temperatures, for example in winter. This range reduction, also referred to as range loss, is mainly caused by the fact that in cold ambient conditions a large amount of electrical energy must be used to heat the interior, also referred to as the vehicle cabin. Compared to conventional drive trains with combustion engines, electric drive trains have very low heat losses. However, these heat losses are no longer available to heat the cabin. The missing heat losses must be compensated for, for example, with the help of electric auxiliary heaters to heat the cabin.This means that it is advantageous to utilize technically unavoidable, remaining losses as efficiently as possible to heat the interior. Waste heat generated in the electric drive system can be used alternatively or additionally, for example, to precondition an electrical energy storage device for charging the electrical energy storage device, i.e., to control its temperature, in particular, to heat it, which is also conventionally done using an auxiliary electric heater. For example, electrical energy can be stored, in particular electrochemically, in the electrical energy storage device, which can be used to supply the electrical machine, for example.

[0018] Conventional solutions only have the first heat exchanger, which, when the first fluid is oil and the second fluid contains at least or exclusively water, is also referred to as an oil-water heat exchanger. For example, the first fluid can be used to cool at least part of the electric machine and, for example, a transmission via which, for example, the motor vehicle is driven by the electric machine. After cooling the electric machine and, if applicable, the transmission, the first fluid flows into a reservoir and collects there, forming a sump, for example, an oil sump. The first fluid can be sucked in from the reservoir or sump and guided over the first heat exchanger, i.e., conveyed through the first heat exchanger. However, the first fluid usually loses absorbed heat to a housing, the sump, the environment, etc., which usually leads to excessive heat losses. A conventional path from the generation of waste heat to its use to heat the interior therefore has a high number of heat transfers and thermal sinks and is therefore sluggish and inefficient in a transient situation. Conventionally, the only way to achieve advantageously strong heating of the interior is usually to achieve a particularly high volume flow of the first fluid through the first circuit. However, when the temperature cools down or is low and the viscosity of the first fluid is therefore high, this is accompanied by high losses in a pump for pumping the first fluid. One challenge is usually that the maximum continuous output of the electric drive device, in particular of the electric machine, depends significantly on the component temperatures of the electric machine.These depend on the maximum volume flow of the first fluid and the temperature of the second fluid, particularly at or in the first heat exchanger. This temperature can be up to 65°C, so that a temperature difference is very small at a temperature of the first fluid in the sump of, for example, 80°C. The aforementioned problems and disadvantages can now be avoided by the invention. Particularly at cold ambient temperatures, the invention allows the technically unavoidable heat generated in the electric drive system, also referred to as waste heat, which is transferred to the first fluid to be efficiently utilized, for example, to heat the interior.

[0019] In order to be able to realize a particularly energy-efficient and demand-oriented operation, it is provided in one embodiment of the invention that an electrically operated pump, for example, is arranged in the first circuit, by means of which the first fluid can be conveyed through the first circuit.

[0020] According to the invention, at least the aforementioned part of the electric machine is arranged in the first circuit and is thus to be lubricated and / or cooled by means of the first fluid. This ensures particularly efficient operation.

[0021] In order to operate the electric drive device and thus the motor vehicle particularly efficiently, a further embodiment of the invention provides that the first heat exchanger is arranged downstream of the pump and upstream of the part in the first circuit in the flow direction of the fluid flowing through the first circuit, which, for example, flows through the first circuit in the said flow direction during operation of the electric drive device. For example, during operation of the electric drive device, the first fluid is pumped through the first circuit in the flow direction by means of the pump.

[0022] The part, also referred to as the machine part, has, for example, a machine inlet, via which the first fluid can be supplied to the part, in particular introduced into the part. In addition, the part has, for example, a machine outlet, via which the first fluid can be discharged from the part, in particular discharged from the part. With respect to the aforementioned flow direction, the machine outlet is thus arranged downstream of the machine inlet. In other words, the first fluid flows on its way through the first circuit from the machine inlet to the machine outlet and thereby through the part. Thus, it is preferably provided that the first heat exchanger is arranged downstream of the pump and upstream of the machine inlet, thus between the pump and the machine inlet in the first circuit, in particular with respect to the aforementioned flow direction.

[0023] A further embodiment of the invention is characterized in that the second heat exchanger is arranged downstream of the part and upstream of the pump in the first circuit, which, for example, allows for particularly efficient operation. In other words, it is preferably provided that the second heat exchanger is arranged downstream of the machine outlet and upstream of the pump in the first circuit, so that the second heat exchanger is preferably arranged between the machine outlet and the pump.

[0024] In a further, particularly advantageous embodiment of the invention, the second heat exchanger is arranged in the first circuit downstream of the part, in particular downstream of the machine outlet, and upstream of the aforementioned reservoir arranged in the first circuit, in which the first fluid can be received to form the aforementioned sump. The pump is preferably arranged upstream of the first heat exchanger and downstream of the reservoir in the first circuit.

[0025] Thus, for example, the second heat exchanger is arranged downstream of the part, in particular downstream of the machine outlet, and upstream of the reservoir, thus between the machine outlet and the reservoir in the first circuit, so that, for example, the second heat exchanger is arranged in a return line of the first circuit, via whose return line the first fluid is to be conducted from the part, in particular from the machine outlet, to and into the reservoir. Thus, for example, the return line runs from the machine outlet to the reservoir with respect to the aforementioned flow direction, thus downstream of the machine outlet and upstream of the reservoir.

[0026] To enable particularly efficient operation of the electric drive device, a further embodiment of the invention provides that the part comprises a rotor of the electric machine and a stator of the electric machine. This means that the electric machine comprises the stator and the rotor, which is drivable by means of the stator and thus rotatable relative to the stator about a machine rotation axis. In particular, the electric machine can provide drive torques via its rotor for driving the motor vehicle, in particular purely electrically.

[0027] It has proven particularly advantageous if the first circuit, especially in the electric machine, branches into a rotor branch and a stator branch, with the rotor branch and the stator branch connected in parallel flow terms. The rotor is arranged in the rotor branch, and the stator is arranged in the stator branch. This allows for efficient and effective cooling of both the rotor and the stator, thus enabling particularly efficient operation.

[0028] It has proven particularly advantageous if the first circuit branches into the rotor branch and the stator branch at a branching point. Preferably, a valve element is arranged in the rotor branch in the flow direction of the first fluid flowing through the first circuit, downstream of the branching point and upstream of the rotor, by means of which valve element the amount of the first fluid flowing through the rotor branch can be adjusted. The valve element is provided, for example, as a control valve, thus as a control valve device. As a result, for example, the amount of the first fluid flowing through the rotor branch can be adjusted as needed, thus enabling particularly efficient operation.

[0029] The branching point is arranged, for example, in the flow direction of the first fluid flowing through the first circuit in the first circuit downstream of the first heat exchanger and in particular in the part or upstream of the part.

[0030] A further embodiment of the invention is characterized in that, in the flow direction of the first fluid flowing through the first circuit, downstream of the second heat exchanger and upstream of the pump, in particular upstream of the reservoir, a branching point of the first circuit is arranged, which has a first branch and a second branch at the branching point. For example, the first branch and the second branch are branches of the aforementioned return line, which branches, for example, at the branching point into the first branch and the second branch. The first branch and the second branch are connected in parallel to one another in terms of flow technology. The aforementioned transmission, for example, is arranged in the second branch, such that the transmission can be supplied with the first fluid via the second branch. The transmission can thus be lubricated and / or cooled by means of the first fluid.The first branch bypasses the transmission, so that the transmission can be bypassed via the first branch by the fluid flowing through the first branch. This means that the first fluid flowing through the first branch does not flow through the second branch and therefore not through the transmission. For example, the first fluid flowing through the first branch can be guided via the first branch into the reservoir, bypassing the second branch and therefore bypassing the transmission. By means of the second branch, for example, the first fluid flowing through the branch and therefore the transmission can be guided into the reservoir, so that, for example, both the first branch and the second branch flow into the reservoir.

[0031] Preferably, a valve device designed, for example, as a pressure relief valve is arranged in the second branch downstream of the branching point and upstream of the transmission, by means of which, for example, a quantity of the first fluid flowing through the second branch can be adjusted.

[0032] A further embodiment of the invention is characterized in that the first heat exchanger is arranged in the first circuit downstream of the pump and upstream of the part, in particular upstream of the machine inlet, in the flow direction of the first fluid flowing through the first circuit, wherein the second heat exchanger is arranged in the first circuit downstream of the pump and upstream of the part, in particular upstream of the machine inlet, in the flow direction of the first fluid flowing through the first circuit. For example, in the flow direction of the fluid flowing through the first circuit, the second heat exchanger is arranged downstream of the first heat exchanger in the first circuit. Thus, both heat exchangers are preferably arranged downstream of the pump and upstream of the part, in particular the machine inlet, in the first circuit, whereby particularly efficient operation can be achieved.

[0033] Preferably, a switching valve is arranged in the first circuit, which is arranged, for example, downstream of the pump and upstream of the first heat exchanger and upstream of the second heat exchanger in the first circuit. The switching valve can be switched between at least two switching states, namely a first switching state and a second switching state, in particular by electrically controlling the switching valve. The first switching state is designed to cause the first fluid to flow through the first heat exchanger and through the second heat exchanger and, for example, through the part in a respective first direction.The second switching state is designed, for example, to cause the first fluid to flow through the first heat exchanger and through the second heat exchanger, and preferably also through the part, in a respective second direction opposite to the respective first direction. Thus, for example, in the first switching state, the pump, the first heat exchanger, the second heat exchanger, and the part are interconnected by means of the switching valve in such a way that, in the flow direction of the first fluid flowing through the first circuit, the first heat exchanger is arranged downstream of the pump and upstream of the second heat exchanger, the second heat exchanger is arranged downstream of the first heat exchanger and upstream of the part, and the part is arranged downstream of the second heat exchanger and upstream of the pump.In the second switching state, the pump, the first heat exchanger, the second heat exchanger, and the part are interconnected by means of the switching valve such that, in the flow direction of the first fluid flowing through the first circuit, the part is arranged downstream of the pump and upstream of the second heat exchanger, the second heat exchanger is arranged downstream of the part and upstream of the first heat exchanger, and the first heat exchanger is arranged downstream of the second heat exchanger and upstream of the pump. Thus, in the first switching state, the first fluid conveyed through the first circuit by the pump in the flow direction flows from the pump, first through the first heat exchanger, then through the second heat exchanger, then through the part, and then, for example, back through the pump.Furthermore, in the second switching state, the first fluid conveyed by the pump in the flow direction through the first circuit flows from the pump, first through the part of the electric machine, then through the second heat exchanger and then through the first heat exchanger and then, in particular, back through the pump. For example, in the first switching state, after flowing through the part, the first fluid flows into the reservoir and can then flow from the reservoir back to the pump and through the pump. For example, in the second switching state, after flowing through the second heat exchanger, the first fluid flows into the reservoir and from there, for example, back to the pump and through the pump.

[0034] A second aspect of the invention relates to a motor vehicle, also simply referred to as a vehicle, which has at least one electric drive device according to the first aspect of the invention and can be driven, in particular purely electrically, by means of the electric drive device. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention, and vice versa.

[0035] A third aspect of the invention relates to a method for operating an electric drive device according to the first aspect of the invention. Advantages and advantageous embodiments of the first aspect and the second aspect of the invention are to be regarded as advantages and advantageous embodiments of the third aspect of the invention, and vice versa.

[0036] Further advantages, features, and details of the invention will become apparent from the following description of preferred embodiments and from the drawings. 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 specified combinations, but also in other combinations or on their own, without departing from the scope of the invention.

[0037] The drawing shows: Fig. 1 is a schematic representation of a first embodiment of an electric drive device for a motor vehicle; Fig. 2 a schematic representation of a second embodiment of the electric drive device; Fig. 3 a schematic representation of a third embodiment of the electric drive device; Fig. 4 a schematic representation of a fourth embodiment of the electric drive device; Fig. 5 is a schematic representation of a fifth embodiment of the electric drive device; Fig. 6 a schematic representation of a sixth embodiment of the electric drive device; Fig. 7 a schematic representation of a seventh embodiment of the electric drive device; Fig. 8 is a schematic representation of an eighth embodiment of the electric drive device; Fig. 9 is a schematic representation of a ninth embodiment of the electric drive device; Fig. 10 is a schematic representation of a tenth embodiment of the electric drive device; Fig. 11 is a schematic representation of an eleventh embodiment of the electric drive device; Fig. 12 is a schematic representation of a twelfth embodiment of the electric drive device; and Fig. 13 is a block diagram illustrating a method for operating the electric drive device.

[0038] In the figures, identical or functionally identical elements are provided with the same reference numerals.

[0039] Fig. 1 shows a schematic representation of a first embodiment of an electric drive device 10 of a motor vehicle, also referred to simply as a vehicle, whose interior, also referred to as a passenger cell, passenger compartment or cabin, is formed by a structure of the motor vehicle, for example designed as a self-supporting body. While the motor vehicle is traveling, persons such as the driver of the motor vehicle can be present in the interior. The motor vehicle can be driven by means of the electric drive device 10, in particular purely electrically. For this purpose, the electric drive device 10 has at least or exactly one Fig. 1, the electric machine 12 is illustrated particularly schematically, which has a stator 14 and a rotor 16. The rotor 16 can be driven by the stator 14 and is thus rotatable about a machine rotation axis relative to the stator 14. Via its rotor 16, the electric machine 12 can provide drive torques for driving the motor vehicle, in particular purely electrically. The electric drive device 10 also has an electrical energy storage device 18, which is also referred to as a battery and is preferably designed as a secondary battery. In particular, the electrical energy storage device 18 is designed as a high-voltage battery (HV battery).Electrical energy is to be stored or is stored in the battery, in particular electrochemically, wherein the electrical machine 12 can be supplied with the electrical energy stored in the battery, in particular in order to thereby operate the electrical machine in a motor mode and thus as an electric motor, by means of which the motor vehicle can be driven or is driven, in particular purely electrically.

[0040] The electric drive device 10 has a first circuit 20 through which a lubricant and / or coolant can flow. The lubricant and / or coolant is a first fluid or is also referred to as the first fluid. Thus, during operation of the electric drive device 10, the first fluid flows through the first circuit 20. In the first embodiment, the first fluid is a liquid, in particular an oil, so that the first circuit 20 is also referred to as an oil circuit or oil circuit. It can be seen that at least one part 22 of the electric machine 12, also referred to as a machine part, is arranged in the first circuit 20 and is thereby to be lubricated and / or cooled by means of the first fluid flowing through the first circuit 20. The part 22 comprises the stator 14 and the rotor 16.This means that the stator 14 and the rotor 16 are arranged in the first circuit 20 and are thus to be lubricated and / or cooled by means of the first fluid.

[0041] The electric drive device 10 also has a second circuit 24, which is at least partially, in particular completely, fluidically separated from the first circuit 20. A second fluid, which is different from the first fluid and is preferably a liquid, can flow through the second circuit 24. This means that, for example, during the aforementioned operation of the drive device 10, the second fluid flows through the second circuit 24. Preferably, the second fluid is or comprises at least or exclusively water. The second fluid is a cooling fluid, which is also referred to as cooling water, particularly when the second fluid comprises at least water or is water. The second circuit 24 is therefore also referred to as a cooling circuit.

[0042] The electric drive device 10 has a first heat exchanger 26, which is arranged in both the first circuit 20 and the second circuit 24 and can thus be flowed through by both the first fluid and the second fluid. Heat can be exchanged between the first fluid and the second fluid via the first heat exchanger 26. This means that, via the heat exchanger 26, heat can either be transferred from the first fluid to the second fluid or heat can be transferred from the second fluid to the first fluid. Thus, the circuits 20 and 24 are thermally coupled to one another via the first heat exchanger 26.

[0043] In order to be able to realize particularly energy-efficient operation of the electric drive device 10 and thus of the motor vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car, the electric drive device 10 has a third circuit 28 which is at least partially, in particular completely, fluidically separated from the first circuit 20 and at least partially, in particular completely, from the second circuit 24. A third fluid that is different from the first fluid and the second fluid can flow through the third circuit 28. This means that, for example, in the aforementioned operation of the drive device 10, the third fluid flows through the third circuit 28. The third fluid is a coolant, so that the third circuit 28 is also referred to as a coolant circuit or coolant circuit.As explained in more detail below, the third circuit 28 is designed to specifically effect changes in the aggregate state of the third fluid. The drive device 10 preferably comprises the first fluid, the second fluid, and the third fluid, which are thus preferably components of the drive device 10.

[0044] Furthermore, the electric drive device 10 has a second heat exchanger 30 provided in addition to the first heat exchanger 26, which is arranged both in the first circuit 20 and in the third circuit 28. Thus, the second heat exchanger 30 can be flowed through by both the first fluid and the second fluid. Heat can be exchanged between the first fluid and the third fluid via the second heat exchanger 30, so that, for example, heat can optionally be transferred from the first fluid to the third fluid or heat can be transferred from the third fluid to the first fluid. Thus, the circuits 20 and 28 are thermally coupled to one another via the heat exchanger 30. It can be seen that the heat exchanger 30 is arranged outside the heat exchanger 26 and the heat exchanger 26 is arranged outside the heat exchanger 30, wherein the heat exchangers 26 and 30 are preferably completely spaced from one another.

[0045] Arranged in the first circuit 20 is a pump 32, which can be operated electrically, for example, and is also referred to as an oil pump, particularly when the first fluid is oil. The pump 32 is designed such that, in particular by operating the pump 32, the first fluid is conveyed through itself, i.e. through the pump 32, in particular in a pumping direction, also referred to as the conveying direction, whereby the first fluid can be conveyed through the first circuit 20 in a flow direction by means of the pump 32. With respect to a flow of the first fluid through the pump 32, the conveying direction coincides with the flow direction. Thus, for example, in the aforementioned operation of the drive device 10, the pump 32 is operated, whereby the pump 32 conveys the first fluid through itself in the conveying direction and thereby conveys the first fluid in the flow direction through the first circuit 20.

[0046] Part 22, also referred to as the machine part, has a first connection A1, also referred to as the first machine connection, and a second connection A2, also referred to as the second machine connection. The first fluid can flow through the connections A1 and A2. Part 22, and thus the stator 14 and the rotor 16, are integrated into the first circuit 20 via the connections A1 and A2.

[0047] At the Fig. 1, the first heat exchanger 26 is arranged, in particular always, downstream of the pump 32 and upstream of the part 22, in particular upstream of the connection A1, in the first circuit 20, with respect to the said flow direction in which the pump 32 conveys the first fluid through the first circuit 20 during the said operation of the drive device 10, and thus in which the first fluid flows through the first circuit 20 during the said operation of the drive device 10.

[0048] The aforementioned operation of the drive device 10 is an operating state of the electric drive device 10, also referred to as the first operating state, or is carried out in an operating state of the electric drive device 10, also referred to as the first operating state. When reference is made above and below to the operating state, this shall mean the first operating state unless otherwise stated. Thus, in the first operating state, the pump 32 conveys the first fluid in the flow direction through the first circuit 20, so that in the first operating state, the first fluid flows through the first circuit 20 in the flow direction. The aforementioned flow direction is also referred to as the first flow direction. When reference is made above and below to the flow direction, this shall mean the first flow direction unless otherwise stated.In the first operating state, the pump 32 thus conveys the first fluid in the conveying direction through itself, i.e., through the pump 32, so that in the first operating state the first fluid flows in the conveying direction through the pump 32. This is to be understood in particular that the pump 32 has a pump housing and a conveying element which is movable, in particular rotatable, relative to the pump housing and by means of which the first fluid can be conveyed by driving the conveying element and thus conveyed through the pump 32, i.e., through the pump housing, so that in the first operating state the first fluid flows through the pump housing in the conveying direction, thus in the first operating state the pump 32 conveys the first fluid in the conveying direction through itself, i.e., through the pump housing.At least with respect to a flow of the first fluid through the pump 32, i.e. through the pump housing, the conveying direction coincides with the flow direction.

[0049] In the first embodiment, the second heat exchanger 30 is arranged downstream of the part 22 and thus downstream of the stator 14 and the rotor 16 and upstream of the pump 32 in the first circuit 20 with respect to the flow direction.

[0050] The electric drive device 10 has a reservoir 34 in which the first fluid can be at least temporarily absorbed to form a sump. In particular, when the first fluid is in the form of oil, the sump is also referred to as an oil sump. It can be seen that, with respect to the flow direction, in the first embodiment, the reservoir 34 and thus the sump is arranged downstream of the heat exchanger 30 and upstream of the pump 32 in the first circuit 20. Thus, the second heat exchanger 30 is arranged downstream of the part 22 and upstream of the reservoir 34 in the first circuit 20 with respect to the flow direction. With respect to the flow direction, in the first embodiment, the pump 32 is arranged upstream of the first heat exchanger 26 and downstream of the reservoir 34 in the first circuit 20.

[0051] The first circuit 20 branches, in particular at a branching point AS, into a rotor branch RZ and a stator branch SZ, wherein the stator branch SZ and the rotor branch RZ are connected in parallel flow terms. The stator 14 is arranged in the stator branch SZ, and the rotor 16 is arranged in the rotor branch RZ, so that the stator 14 and the rotor 16 are connected in parallel flow terms.

[0052] A first valve V1, which is designed, for example, as a shut-off valve or a shut-off valve, is arranged in the third circuit 28. The first valve V1 can be switched, in particular moved, between a closed state that fluidically blocks the circuit 28 and an open state that releases the circuit 28.

[0053] A second valve V2, also referred to as a valve element, is arranged in the rotor branch RZ downstream of the branching point AS and upstream of the rotor 16. By means of this valve, a quantity of the first fluid flowing through the rotor branch RZ, thus a quantity of the first fluid flowing through the rotor branch RZ, can be adjusted. In the first embodiment, for example, the second valve V2 is designed as a control valve.

[0054] Out of Fig. 1 also shows that the first circuit 20 has a return line 36, via which the first fluid is to be guided from the part 22 to and into the reservoir 34. The return line 36 thus runs downstream of the part 22 and upstream of the reservoir 34 with respect to the flow direction. It can be seen that the heat exchanger 30 is arranged in the return line 36, so that the first fluid flowing from the part 22 to and into the reservoir 34 can flow through the heat exchanger 30. Thus, the first fluid can exchange heat with the third fluid on its way from the part 22 to and into the reservoir 34 via the heat exchanger 30.

[0055] The electric drive device 10 also has a Fig. 1 has a particularly schematically illustrated gear 38, via which the motor vehicle can be driven by the electric machine 12, in particular the rotor 16. The gear 38 is arranged in the first circuit 20 and is thus to be lubricated and / or cooled by means of the first fluid. For this purpose, in the first embodiment, the return line 36 of a branching point VZ branches into a first branch Z1 and a second branch Z2, wherein the branching point VZ is arranged downstream of the heat exchanger 30 and upstream of the gear 38 and thus upstream of the reservoir 34 with respect to the flow direction. The branches Z1 and Z2 are connected in parallel to one another in terms of flow technology. The gear 38 is arranged in the second branch Z2 downstream of the branching point VZ and upstream of the reservoir 34 and can thus be supplied with the first fluid flowing through the second branch Z2.The first fluid flowing through branches Z1 and Z2 can be introduced to and into reservoir 34 via branches Z1 and Z2, so that, for example, in the first embodiment, branches Z1 and Z2 open into reservoir 34. Branches Z1 and Z2 thus run downstream of heat exchanger 30 and upstream of reservoir 34 with respect to the flow direction, so that transmission 38 is arranged in first circuit 20, in particular in second branch Z2, upstream of reservoir 34 and downstream of heat exchanger 30 with respect to the flow direction, in particular downstream of branching point VZ.

[0056] In the first embodiment, a third valve V3, which is designed, for example, as a shut-off valve, is arranged in the second branch Z2 downstream of the branching point VZ and upstream of the transmission 38 with respect to the flow direction. The aforementioned closed state is also referred to as the first closed state, blocked state or first blocked state, and the aforementioned open state is also referred to as the first open state, released state or first released state. The third valve V3 can be switched, i.e. adjusted, between a second blocked state and a second open state, wherein the second open state is also referred to as the second released state and the second blocked state is also referred to as the second closed state. In the second closed state, the branch Z2 is fluidly blocked by the valve V3, and in the second open state, the third valve V3 releases the branch Z2.

[0057] In the first embodiment, with respect to the first fluid flowing through the stator 14 and thus the stator branch SZ and the first fluid flowing through the rotor 16 and thus the rotor branch RZ, only the first fluid flowing through the stator 14 and thus the stator branch SZ can be guided to the heat exchanger 30. In other words, with respect to the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16, only the first fluid flowing through the stator 14 can flow through the heat exchanger 30.The first fluid flowing through the rotor 16 and thus the rotor branch RZ bypasses both the heat exchanger 30 and the return line 36 and thus the gear 38 and the valve V3 and the branches Z1 and Z2, so that the first fluid flowing through the rotor 16 and thus the rotor branch RZ on its way from the rotor 16, in particular from the branching point AS, to and into the reservoir 34 does not flow through the heat exchanger 30 and not through the gear 38, but bypasses both the heat exchanger 30 and the gear 38.In the first embodiment, the first circuit 20 has a connecting line 40, which is fluidically connected at a connection point VS1 to the return line 36 running downstream of the stator 14 and upstream of the reservoir 34. With respect to the first fluid flowing through the stator 14 and thus the stator branch SZ and the first fluid flowing through the rotor 16 and thus the rotor branch RZ, the connecting line 40 is exclusively capable of being flowed through by the first fluid flowing through the stator 14 and thus the stator branch SZ. Furthermore, the connecting line 40 is fluidically connected to the rotor branch RZ at a second connection point VS2.

[0058] With respect to the flow direction, the connection point VS1 is arranged upstream of the heat exchanger 30 and downstream of the stator 14, in particular in the return line 36. With respect to the flow direction, the connection point VS2 is arranged in the rotor branch RZ downstream of the branching point AS and upstream of the rotor 16, in particular upstream of the second valve V2. It can be seen that a check valve RV is arranged in the connecting line 40, which opens, in particular independently, in the direction of the rotor branch RZ and closes, in particular independently, in the direction of the return line 36. As a result, the first fluid can flow from the return line 36 into the rotor branch RZ via the check valve RV, although the check valve RV, in particular independently, i.e. automatically, prevents a flow of the first fluid from or out of the rotor branch RZ into the return line 36.

[0059] The interior of the vehicle is in Fig. 1 is shown particularly schematically and designated 42. A second pump 44 is arranged in the second circuit 24, by means of which the second fluid can be pumped through the circuit 24. A third heat exchanger 46, also referred to as a radiator or vehicle radiator, is arranged in the circuit 24, which third heat exchanger is arranged downstream of the battery and upstream of the pump 44 in the flow direction of the second fluid flowing through the circuit 24. A fan 48, which can be operated electrically, in particular, is designed to convey air that can flow around the heat exchanger 46, so that heat can be exchanged between the air flowing around the heat exchanger 46 and the second fluid via the heat exchanger 46. For example, power electronics 50 is arranged in the circuit 24, via which power electronics, for example, can be supplied to the electric machine 12 with electrical energy.In the flow direction of the second fluid flowing through the circuit 24, the power electronics 50 are arranged upstream of the heat exchanger 26 and downstream of the pump 44 in the circuit 24. The heat exchanger 46 is arranged downstream of the heat exchanger 26 and upstream of the pump 44 in the circuit 24. A fourth heat exchanger 52 is arranged in the circuit 24, which is also arranged in the circuit 28. In the flow direction of the second fluid flowing through the circuit 24, the heat exchanger 52 is arranged downstream of the heat exchanger 26 and upstream of the heat exchanger 46 in the circuit 24. The circuit 24 has a branch Z3 and a branch Z4. The pump 44, the heat exchanger 46, the power electronics 50, the heat exchanger 26, the heat exchanger 52, and a fifth valve V5 are arranged in branch Z3. The electrical energy storage device 18 and the fifth valve V5 are arranged in the branch Z4.Branch Z4 is connected to branch Z3 at a connection point VS3 and at a connection point VS4, wherein connection point VS3 is arranged downstream of pump 44 and downstream of heat exchanger 46, and upstream of heat exchanger 26 and upstream of power electronics 50 in the flow direction of the second fluid flowing through circuit 24. Connection point VS4 is arranged upstream of heat exchanger 46 and downstream of heat exchanger 52 in the flow direction of the second fluid flowing through circuit 24. The fifth valve V5 can be switched, in particular moved, between a first switching state S1 and a second switching state S2.In the first switching state S1, at least or exclusively a first portion of the second fluid flowing through branch Z3 is branched off from branch Z3 at connection point VS3 and introduced into branch Z4 and guided to the battery via valve V5, so that the battery can be or is supplied with the first portion of the second fluid. A second portion of the second fluid can flow through power electronics 50, heat exchanger 26, and heat exchanger 52 and subsequently flow via valve V5 to connection point VS4. The first portion can also flow from the battery to connection point VS4, where the first portion and second portion combine to form a single portion, which flows through heat exchanger 46 and pump 44 and then flows back to connection point VS3.In the second switching state S2, the second fluid does not branch off from the branch Z3 at the connection point VS3, but the entire second fluid flowing through the heat exchanger 46 and the pump 44 flows from the connection point VS3 through the power electronics 50, the heat exchanger 26 and the heat exchanger 52 and through the valve V5 and from the valve V5 through the battery and from there to the connection point VS4 and from there again to and through the heat exchanger 46. It can be seen that in the switching state S1 the second part of the second fluid bypasses the battery and therefore does not flow through the battery.

[0060] In the third circuit 28, for example, Fig. 1, devices 54 are arranged, which are shown particularly schematically and by means of which, for example, the aforementioned change in the state of aggregation of the third fluid can be brought about. A first of the devices 54 is, for example, a refrigerant compressor, by means of which the refrigerant (third fluid) can be conveyed through the third circuit 28 and compressed. A second of the devices 54 is, for example, an expansion element, designed, for example, as an expansion valve, for expanding the refrigerant. The heat exchanger 52 is, for example, also referred to as a chiller. For example, in particular in a heat pump operating mode of the circuit 28, also referred to as heat pump operation, heat can be transferred from the second fluid to the third fluid via the chiller, whereby the second fluid is cooled and the third fluid is heated.Also arranged in the third circuit 28 is a fourth heat exchanger 56, which may, for example, be one of the devices 54, in particular a third of the devices 54. The heat exchanger 56 can, for example, be operated either as a cooler, in particular a condenser, for cooling and, for example, condensing the third fluid, or as an evaporator for evaporating the third fluid. For example, in heat pump mode, the heat exchanger 56 can be or is operated as a cooler, in particular a condenser, by means of which the third fluid is to be cooled or is cooled. By cooling the third fluid in this way, the third fluid can, for example, be condensed. The circuit 28 can, for example, be operated in heat pump mode and, for example, in a cooling mode, which is also referred to as cooling mode.In the cooling mode, for example, the heat exchanger 56 is or is operated as an evaporator, by means of which the third fluid is or is to be evaporated.

[0061] It can be seen that air, also referred to as cabin air, can flow around the heat exchanger 56, whereby the cabin air can be introduced or is introduced into the interior space 42. Heat can be exchanged between the cabin air and the third fluid via the heat exchanger 56. If the heat exchanger 56 is operated, for example, as the aforementioned cooler, heat is transferred from the third fluid to the cabin air via the heat exchanger 56, as a result of which the cabin air is heated and the third fluid is cooled. This is particularly the case in heat pump operation. Since the heated cabin air can be introduced or is introduced into the interior space 42, the interior space 42 can be warmed, i.e., heated. If the heat exchanger 56 is operated, for example, as the aforementioned evaporator, heat can be transferred from the cabin air to the third fluid via the heat exchanger 56, as a result of which the cabin air is cooled and the third fluid is heated.The cooled cabin air can be introduced into the interior 42, thereby cooling the interior 42. This is particularly intended or the case in the cooling operating mode.

[0062] Fig. 2 shows a second embodiment of the drive device 10. The second embodiment differs from the first embodiment in particular in that, in the second embodiment, the heat exchanger 30 can be flowed through by both the first fluid flowing through the stator 14 and the first fluid flowing through the stator 15 with respect to the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16.For this purpose, in contrast to the first embodiment, the rotor branch RZ does not bypass the heat exchanger 30 and the gear 38, but the stator branch SZ and the rotor branch RZ are joined at a joining point ZS and thereby combined to form the return line 36, which thus runs downstream of the rotor 16 and downstream of the stator 14 and thus downstream of the part 22 and upstream of the reservoir 34 and can therefore be flowed through by both the first fluid flowing through the stator 14 and thus the stator branch SZ and the first fluid flowing through the rotor 16 and thus the rotor branch RZ. As in the first embodiment, the second valve V2 is arranged in the rotor branch RZ downstream of the branching point AS and upstream of the rotor 16.In summary, in the first embodiment, the return line 36 runs downstream of the stator 14 and upstream of the reservoir 34 and, with respect to the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16, can only be flowed through by the first fluid flowing through the stator 14, so that in the first embodiment, the heat exchanger 30 can only be flowed through by the first fluid flowing through the stator 14 with respect to the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16.In the second embodiment, the return line 36 runs downstream of the stator 14 and downstream of the rotor 16, and thus downstream of the part 22 as a whole, and upstream of the reservoir 34, and can be flowed through by both the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16, wherein the heat exchanger 30 arranged in the return line 36 can be flowed through by both the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16. In other words, in the second embodiment, both the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16 flow through the heat exchanger 30 on its way from the stator 14 and from the rotor 16 to the reservoir 34.

[0063] Fig. 3 shows a third embodiment of the drive device 10. In the third embodiment, the first valve V1 is a changeover valve, the function of which will be explained in more detail below. In the third embodiment, the valve V1 can be switched, in particular moved, between a third switching state S3 and a fourth switching state S4. In the third embodiment, the drive device 10 has a fourth valve V4, which can be switched, in particular moved, between a fifth switching state S5 and a sixth switching state S6. The valve V4 is arranged in the second circuit 24. The drive device 10 also comprises a sixth valve V6, which can be switched, in particular moved, between a seventh switching state S7 and an eighth switching state S8. In the third embodiment, the heat exchangers 26 and 30 are arranged fluidically between the pump 32 and the part 22 of the electric machine 12.In summary, in the third embodiment, in the third switching state S3 of the valve V1, the heat exchangers 26 and 30 are arranged downstream of the pump 32 and upstream of the part 22 in the flow direction of the first fluid flowing through the circuit 20, such that the heat exchanger 26 is arranged downstream of the pump 32 and upstream of the heat exchanger 30, and the heat exchanger 30 is arranged downstream of the heat exchanger 26 and upstream of the part 22. Thus, in the third switching state S3 of the valve V1, the first fluid flowing through the circuit 20, particularly in the flow direction, flows from the pump 32 first through the heat exchanger 26 and then through the heat exchanger 30 and then through the part 22.In the fourth switching state S4 of the valve V1, the heat exchangers 26 and 30 are arranged downstream of the part 22 and upstream of the pump 32 in the flow direction of the first fluid flowing through the circuit 20, such that the heat exchanger 30 is arranged downstream of the part 22 and upstream of the heat exchanger 26, and the heat exchanger 26 is arranged downstream of the heat exchanger 30 and upstream of the pump 32. Thus, in the fourth switching state S4 of the valve V1, the first fluid flowing through the circuit 20, particularly in the flow direction, flows from the pump 32 first through the part 22 and then through the heat exchanger 30, whereupon the first fluid flows through the heat exchanger 26.In other words, the pump 32 conveys the first fluid through itself in the conveying direction, whereby the pump 32 conveys the first fluid through the circuit 20, while the valve V1 is in the third switching position S3, the first fluid flows from the pump 32 via the valve V1 first to the heat exchanger 26 and through the heat exchanger 26, whereupon the first fluid flows through the heat exchanger 30. The first fluid then flows through the part 22, whereupon the first fluid flows into the reservoir 34 and from there back to and through the pump 32.If the pump 32 pumps the first fluid through itself in the pumping direction, whereby the pump 32 pumps the first fluid through the circuit 20 while the valve V1 is in the fourth switching state S4, the first fluid flows from the pump 32 via the valve V1 first to and through the part 22, whereupon the first fluid flows through the heat exchanger 30. From there.

[0064] The first fluid flows through heat exchanger 30 to and through heat exchanger 26, whereupon the first fluid flows, in particular via valve V1, to and into reservoir 34 and from there again to and through pump 32. In the third switching state S3, the first fluid flows in a respective first direction on its way through heat exchangers 26 and 30 and through part 22. In the fourth switching state S4, the first fluid flows in a respective second direction, opposite to the respective first direction, on its way through heat exchangers 26 and 30 and part 22, so that in the fourth switching state S4, a reversal of flow direction is created compared to the third switching state S3.The flow direction reversal provides that the first fluid flows in the respective first direction through the heat exchangers 26 and 30 and the part 22 in the fourth switching state S4, wherein the first fluid flows in the respective second direction, opposite to the respective first direction, through the heat exchangers 26 and 30 and the part 22 in the fourth switching state S4. For example, the valve V1 is in the third switching state S3 in the aforementioned first operating state.For example, in a second operating state of the drive device 10, the valve V1 is in the fourth switching state S4, so that, for example, in the second operating state, the pump 32 conveys the first fluid in the conveying direction through the pump 32, whereby the first fluid is conveyed in the flow direction through the circuit 20 and flows through the circuit 20 in such a way that the first fluid flows from the pump 32 via the valve V1, first to the heat exchanger 26 and flows through the heat exchanger 26, whereupon the fluid flows through the heat exchanger 30, whereupon the fluid flows through the part 22. The fluid then flows to the reservoir 34 and through the reservoir 34 and back to the pump 32.In the first operating state, the pump 32 conveys the first fluid in the flow direction through the pump 32, whereby the first fluid is conveyed through the circuit 20 and flows through the circuit 20 in such a way that the first fluid flows from the pump 32 via the valve V1 first to the part 22 and flows through the part 22, whereupon the fluid flows through the heat exchanger 30. The fluid then flows through the heat exchanger 26, whereupon the fluid flows, in particular via the valve V1, to the reservoir 34, flows through the reservoir 34 and from the reservoir 34 back to and through the pump 32. In the first operating state, the fluid flows from the part 22 via the valve V1 to the reservoir 34. It can also be seen that in the first operating state, the port A1 is arranged upstream of the port A2, so that the first fluid flows from the port A1 to the port A2.Thus, in the first operating state, part 22 is supplied with the first fluid via port A1, and in the first operating state, the first fluid is discharged from part 22 via port A2. In the second operating state, however, port A2 is arranged upstream of port A1, so that in the second operating state, part 22 is supplied with the first fluid via port A2. This means that in the second operating state, the first fluid flows from port A2 to port A1, and in the second operating state, the first fluid is discharged from part 22 via port A1 and fed to the heat exchangers 26 and 30.

[0065] Valve V6, for example, is designed as a shut-off valve. In the seventh switching state S7, valve V6 blocks the fluid flow to circuit 28. In the eighth switching state S8, valve V6 opens circuit 28.

[0066] By means of the fourth valve V4, a reversal of the flow direction of the second fluid through the heat exchanger 26 can be effected. If the pump 44 conveys the second fluid in one flow direction through the pump 44, such that the pump 44 conveys the second fluid through the circuit 24, while the valve V4 is in the fifth switching state S5, the second fluid subsequently flows through the heat exchanger 26 in a first heat exchange direction. If the pump 44 conveys the second fluid in the aforementioned direction, i.e. in the same flow direction through itself, such that the pump 44 conveys the second fluid through the second circuit 24, while the fourth valve V4 is in the sixth switching state S6, the second fluid subsequently flows through the heat exchanger 26 in a second heat exchange direction opposite to the first heat exchange direction.This makes it possible, for example, for the second fluid to flow through the heat exchanger 26 to be counter to the first fluid flow through the heat exchanger 26, and vice versa, both in the third switching state S3 and in the fourth switching state S4 of the valve V1. This ensures particularly advantageous heat exchange.

[0067] The drive device 10 also has a filter 58 arranged in the first circuit 20 and designed, for example, as an oil filter, by means of which the first fluid can be filtered. In the flow direction of the fluid flowing through the circuit 20, the filter 58 is arranged downstream of the reservoir 34 and upstream of the pump 32.

[0068] Fig. 4 shows a fourth embodiment of the electric drive device 10. While in the third embodiment, as in the first embodiment, the first fluid flowing through the rotor 16 and thus the rotor branch RZ bypasses the gear 38 and, for example, also the valve V3 on its way from the rotor 16 to and into the reservoir 34, so that the gear 38 can be supplied exclusively with the first fluid flowing through the stator 14 with respect to the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16, in the fourth embodiment, as in the second embodiment, the stator branch SZ and the rotor branch RZ are brought together at the junction point ZS. In this case, both the first fluid flowing through the stator 14 and the first fluid flowing through the rotor 16 can flow through the gear 38 and, in this case, also the valve V3 on its way to the reservoir 34. Fig. 4 is that in the fourth embodiment the merging point ZS coincides with the branching point VZ. In the third embodiment the connecting point VS2 coincides with the branching point VZ. In the third embodiment and in the fourth embodiment the return line 36 branches at the branching point VZ into the branches Z2 and Z1, wherein the gear 38 and in this case also the valve V3 are arranged in branch Z2. Via branch Z1 the gear 38 can be bypassed by at least part of the first fluid, so that the first fluid flowing through branch Z1 bypasses the gear 38 on its way from the branching point VZ to the reservoir 34, and therefore does not flow through the gear 38.

[0069] Fig. 13 shows a block diagram illustrating a method for operating the electric drive device 10. For example, in the method, the drive device 10 is operated, in particular during a first period of time, in the first operating state and, in particular during a second period of time, in the second operating state, wherein, for example, the second period of time follows the first period of time or precedes the first period of time. In a block B1, a decision is made as to whether the heat pump operating mode, also referred to as heat pump mode, should be requested or not.If, for example, a measured temperature prevailing in the interior 42, also referred to as the cabin temperature, is lower than a specified target value, and a person such as the driver of the motor vehicle has activated air conditioning to condition the interior 42, then block B1 outputs a positive bit, so that, for example, a decision is made that heat pump mode should be requested. In block B2, a decision is made as to whether or not battery auxiliary heating should be requested to heat the battery in order to achieve particularly efficient operation.If a current battery temperature, particularly a measured one (also referred to as battery temperature), is lower than a corresponding target temperature, which is calculated, for example, from a characteristic map that depends on a current state of charge and a temperature prevailing in the vehicle's surroundings (also referred to as ambient temperature), two functions are activated. The first of these functions calculates a potential loss of efficiency due to the heating of the battery, which can be achieved by means of the battery heating mode and is also referred to as auxiliary heating.Since, for example, in the battery heating mode, the electric machine 12 is operated in a power wasting mode, in which a targeted operation of the electric machine 12 with a lower efficiency of the machine 12 than a possible efficiency of the electric machine 12, in order to thereby heat waste heat to heat the battery, and the stator 14 becomes particularly warm as a result, an efficiency disadvantage of the electric machine 12 or of the drive device 10 as a whole occurs. In a second of the functions, a potential efficiency gain is calculated that can be realized by heating the battery by means of the battery heating mode. If the potential efficiency loss is less than the potential efficiency gain, block B2 outputs a positive bit, thus deciding that the battery heating mode should be requested.In a third block B3, a decision is made as to whether battery heating should be requested predictively, for example to shorten the charging time during rapid charging. A vehicle's navigation system, for example, predicts whether rapid charging is imminent, for example at a motorway service station, particularly depending on whether a person such as the driver has selected a charging station. Information about the maximum power of the charging station is then also available, for example. Depending on the characteristic map, which depends, for example, on the ambient temperature and, in particular, the current state of charge of the battery, a setpoint specification for optimizing the charging time is provided. The setpoint specification for optimizing the charging time is, for example, a setpoint temperature specification.If the target temperature is higher than, for example, a measured, current, and actual battery temperature, block B3 outputs a positive bit, thus deciding that battery heating operation should be requested predictively. An optionally provided block B4 decides whether a so-called cooling support mode, also known as cooling boost, or cooling boost operation, can be requested in order to avoid possible derating—i.e., excessive loading of the electric machine 12 and / or power limitation of the electric machine 12—at high vehicle speeds and when rotor limitation is imminent.If, for example, a modeled rotor temperature, also referred to as the rotor temperature, is greater than a predefined or predeterminable limit value of, for example, 80°C, and if a temperature of the stator 14, also referred to as the stator temperature, is less than a defined threshold value of, for example, 160°C, it can be concluded that, with a certain probability, rotor limitation is imminent. If, for example, due to higher stationary driving speeds, the battery temperature does not have a maximum cooling requirement and is less than a defined limit temperature, a calculation is made as to the currently possible additional cooling capacity, in particular for the refrigerant circuit, also referred to as the refrigeration circuit, and the additional heat exchanger 30 and / or the chiller.If this currently possible additional cooling capacity is greater than the calculated required cooling capacity to prevent derating, the cooling boost is requested.

[0070] The heat pump mode is a first operating mode, the battery auxiliary heating mode is a second operating mode, and the cooling boost is a third operating mode. For example, the predictive request for the battery auxiliary heating mode can be a fourth operating mode or be regarded as a fourth operating mode. In block B5, for example, a decision is made as to which of the operating modes will be implemented, particularly depending on a prioritization sequence. In other words, in block B5, one of the aforementioned operating modes is selected and implemented, particularly depending on the prioritization sequence. If only the cooling boost is requested, it is selected and activated, and thus implemented. If only the heat pump mode is requested, it is selected and activated, and thus implemented.If only the battery boost operation, also known as battery heating mode, is requested, then this is selected and activated, and therefore carried out. If neither the cooling boost nor the heat pump mode nor the battery boost mode is requested, then an efficiency mode is selected. If several of the operating modes are requested at the same time, the priority is as follows: The cooling boost is prioritized over the heat pump mode, and the heat pump mode is prioritized over the battery heating mode. If the cooling boost, heat pump mode, and battery heating mode are requested at the same time, the cooling boost is carried out. If only the cooling boost and heat pump mode are requested at the same time, the cooling boost mode is carried out. If the heat pump mode and battery heating mode are requested at the same time, the heat pump mode is carried out.If only cooling boost and battery heating mode are requested at the same time, cooling boost mode is implemented.

[0071] In heat pump mode, pump 32 is operated in maximum characteristic map operation with the maximum possible volume flow of the first fluid flowing through stator 14, in particular depending on a viscosity of the first fluid and in particular while maintaining a pivoting capability, in order to achieve the highest possible heat transfer to heat exchanger 30. Pump 44, which is designed, for example, as a water pump or also referred to as a water pump, is operated in heat pump mode with the maximum possible volume flow in order to achieve the highest possible heat transfer to heat exchanger 26. In heat pump mode, the refrigerant compressor is activated, i.e., switched on, to remove heat from circuit 24 and circuit 20 and thus, for example, to transfer from the second fluid and from the first fluid to or onto the third fluid and subsequently to use it, in particular via heat exchanger 56, to heat interior 42.For this purpose, for example, the heat exchanger 56 is operated as the aforementioned cooler, in particular a condenser. In the heat pump mode, for example, the electric machine 12 is operated in an efficiency map mode to generate the lowest possible losses. Furthermore, the following is provided, for example, in the heat pump mode: The valve V1 is in the switching state S4 in order to flow through the two heat exchangers 26 and 30 after the part 22. Thus, waste heat can be dissipated very efficiently, or in a transient sense, quickly, to the interior 42, since no heat is lost via a housing of the drive device 10 or the sump.

[0072] Valve V2, for example, is a control valve with a flow cross-section that can be adjusted, in particular continuously, through which the first fluid can flow. The flow cross-section can be adjusted, for example, in a range from 0 percent up to and including 100 percent, in particular continuously. At 0 percent, the flow cross-section and thus the rotor branch RZ are fluidically blocked. At 100 percent, the flow cross-section has its maximum possible value, so that at 100 percent, the flow cross-section and thus the rotor branch RZ are maximally open.

[0073] Valve V2 is switched to 0 percent in order to avoid additional drag losses in rotor 16 at high volume flows. Because the stator 14 is cool and operated efficiently and is cooled intensively, there is no cooling requirement in rotor 16. Valve V3 is controlled in an efficiency map operation, which means clocked lubrication and cooling of the transmission 38 depending on the speed of rotor 16 and the torque provided by the electric machine 12 via its rotor 16. Valve V4 is in the sixth switching state S6 in order to also direct waste heat from the battery into circuit 24 or circuit 28. Valve V6 is in the switching state S8 in order to activate heat exchanger 30, which then functions as an additional cooler, and to dissipate additional heat via the heat pump.

[0074] In battery heating mode, i.e., in battery auxiliary heating mode, the following is provided: Pump 32 is operated in maximum map mode with the maximum possible volume flow of the first fluid flowing through stator 14, in particular depending on the viscosity while maintaining the pivoting capability, in order to achieve the highest possible heat transfer to heat exchanger 30. Pump 44 is operated with the maximum possible volume flow in order to achieve the highest possible heat transfer, in particular at heat exchanger 26. The refrigerant compressor is deactivated in order to use heat from circuit 24 for the battery, i.e., to heat the battery. If there is an additional heat requirement for the interior 42, this is intercepted by an electric auxiliary heater, by means of which the cabin air is heated using electrical energy.The electric machine 12 is operated in power wasting mode, i.e., in power wasting map operation, in order to deliberately generate waste heat losses and thus waste heat, particularly in the stator 14, in order to heat the battery. The valve V1 is in its fourth switching state S4 in order to flow through the two heat exchangers 26 and 30 downstream of the part 22. In heat pump mode, the valve V1 is also in the switching state S4. This allows waste heat to be introduced into the circuit 24 very efficiently, or more quickly in a transient manner, and thus used to heat the battery. The valve V2 is operated or controlled in power wasting map operation in order to adjust a volume flow of the first fluid flowing through the rotor 16 according to a cooling requirement.Valve V3 is operated or controlled in efficiency map mode, which, for example, means cyclic lubrication and cooling of the transmission 38, particularly depending on the speed and torque. Valve V4 is in switching state S6 to operate the heat exchanger 26 as a counterflow fluid-to-fluid heat exchanger. Valve V5 is in switching state S2 to utilize waste heat from the electric machine 12 to heat the battery, and valve V6 is in switching state S7, for example, to activate the heat exchanger 30, so that an advantageously large amount of heat is available to heat the battery.

[0075] The following is provided in efficiency mode: Pump 32 is operated in minimum map mode with the minimum possible volume flow, in particular depending on the necessary cooling requirement, in order to achieve the most efficient operation possible, in particular so that the power of pump 32 and drag losses of pump 32 can be advantageously kept low. Pump 44 is operated with the minimum possible volume flow, in particular depending on the necessary cooling requirement, in order to achieve the most efficient operation possible, in particular so that the power of pump 44 can be advantageously kept low. The refrigerant compressor is deactivated because it is not needed. Electric machine 12 is operated in efficiency map mode in order to generate the lowest possible losses. Valve V1 is in switching state S3 in order to flow through heat exchangers 26 and 30 upstream of part 22.The first fluid is thus used as cold as possible to cool part 22. Valve V2 is controlled in efficiency map mode, which sets, in particular controls or regulates, a volume flow of the first fluid through the rotor 16 according to a cooling requirement. Valve V3 is controlled in efficiency map mode, which means, for example, clocked lubrication and cooling of the transmission 38 depending on the speed and torque. In other words, the transmission 38, for example, is supplied with the first fluid in a clocked manner. Valve V4 is in switching state S5 in order to operate the heat exchanger 26 as a counterflow fluid-to-fluid heat exchanger. Valve V5 is in switching position S1 in order to be able to dissipate waste heat from the electric machine 12 as directly as possible to the environment of the motor vehicle.The battery has its own circuit, particularly in the form of branch Z4, and can thus also be supplied with a beneficially cold second fluid. Valve V6 is in switching state S7 to activate heat exchanger 30, which, for example, provides a particularly large amount of heat for heating or keeping the battery warm.

[0076] The cooling boost provides the following: The pump 32 is operated in maximum map operation with the maximum possible volume flow of the first fluid flowing through the stator 14, in particular depending on the viscosity and while maintaining the pivoting ability, in order to achieve the highest possible heat transfer at the heat exchanger 30. The pump 44 is operated with the maximum possible volume flow in order to achieve the highest possible heat transfer at the heat exchanger 26. The refrigerant compressor is activated, i.e. switched on, in order to dissipate heat from the circuit 24 and the electric machine 12 and in particular to the heat exchanger 46. By using the refrigerant compressor or the heat pump, additional cooling capacity can be used by deliberately sacrificing efficiency, for example to avoid torque and / or power limitations of the electric machine 12, particularly at high speeds.The electric machine 12 is operated in efficiency map mode to generate the lowest possible losses. The valve V1 is in the switching state S3 in order to flow through both heat exchangers 26 and 30 upstream of the part 22. The first fluid is thus used as cold as possible to cool the part 22. The valve V2 is operated or controlled in a cooling boost map mode, which adjusts, in particular regulates or controls, a volume flow of the first fluid through the rotor 16 according to a cooling requirement. A proportion of the volume flow of the first fluid flowing through the rotor 16 is increased, for example, since the cooling boost is only used when there is a particular imminent limitation of the electric machine 12. The valve V3 is controlled in efficiency map mode, which means, for example, the aforementioned, clocked lubrication and cooling of the transmission 38 depending on the speed and torque.Valve V4 is in switching state S5 to operate heat exchanger 26 as a counterflow fluid-to-fluid heat exchanger. Valve V5 is in switching state S1 to dissipate waste heat from electric machine 12 as directly as possible to the environment. The battery has its own circuit, for example, in the form of branch Z4, and can thus also be flowed through with a beneficially cold second fluid. Valve V6 is in switching state S8 to activate heat exchanger 30, which functions, for example, as an additional cooler, and to dissipate additional heat via the heat pump.

[0077] It can be seen that, for example, the rotor branch RZ can be adjusted, in particular controlled or regulated, as required by means of the valve V2 with regard to the volume flow of the first fluid flowing through the rotor branch RZ, in particular by setting, i.e., adjusting, the flow cross-section in the range from 0 percent up to and including 100 percent, in particular continuously. By selectively switching the valve V3 to the second blocking state or the second open state, the transmission 38 can be supplied with the first fluid as required via the valve V3, whereby the transmission 8 can be lubricated and / or cooled as required.

[0078] Fig. 5 shows a fifth embodiment of the drive device 10. In the fifth embodiment, a seventh valve V7 is arranged in the circuit 28, wherein, for example, the valve V7 is provided alternatively or in addition to the valve V6. The valve V7 can be switched between a ninth switching state S9 and a tenth switching state S10. For example, the switching state S9 corresponds to the switching state S7, wherein, for example, alternatively or additionally, the switching state S10 corresponds to the switching state S8. If the refrigerant compressor is activated, so that the refrigerant compressor pumps the refrigerant through the circuit 28, while the valve V7 is in the switching state S9, the pumped refrigerant, in particular all of it, bypasses the heat exchanger 30, so that the heat exchanger 30 is not flowed through by the refrigerant. As a result, the heat exchanger 30 is deactivated, i.e., switched off.If the refrigerant compressor conveys the refrigerant through the circuit 28 while the valve V7 is in the switching state S10, the refrigerant (third fluid), in particular the entire refrigerant conveyed by the refrigerant compressor, flows through the heat exchanger 30, so that the heat exchanger 30 is activated, i.e. is switched on.

[0079] Fig. 6 shows a sixth embodiment of the drive device 10, Fig. 7 shows a seventh embodiment of the drive device 10, Fig. 8 shows an eighth embodiment of the drive device 10, Fig. 9 shows a ninth embodiment of the drive device 10, Fig. 10 shows a tenth embodiment of the drive device 10, Fig. 11 shows an eleventh embodiment of the drive device 10, and Fig. 12 shows a twelfth embodiment of the drive device 10. In a thirteenth embodiment (not shown in the figures), it is provided, for example, that, in comparison to the fifth embodiment, valve V6, which is designed in particular as a shut-off valve, is provided instead of valve V7. In a fourteenth embodiment (not shown in the figures), it is provided, for example, that, in comparison to the fifth embodiment, valve V2 is omitted, in particular without replacement. In a fifteenth embodiment (not shown in the figures), it is provided, for example, that, in comparison to the fifth embodiment, valve V3 is omitted, in particular without replacement.

[0080] At the Fig. In the sixth embodiment shown in Figure 6, for example, the valve V7 is omitted, in particular without replacement, in comparison to the fifth embodiment. Alternatively, it would be conceivable for the sixth embodiment to provide the valve V7 or, in particular, alternatively, the valve V6. In comparison to the fifth embodiment, the sixth embodiment provides that, instead of the valve V2, a valve V8 is provided, which is designed in particular as a shut-off valve and can be switched between an eleventh switching state S11 and a twelfth switching state S12. In the switching state S12, the rotor branch RZ is fluidically blocked by means of the valve V8, and in the switching state S11, the valve V8 opens the rotor branch RZ for a flow of the first fluid through the rotor branch RZ.

[0081] The fifth embodiment and the sixth embodiment are based, for example, particularly with regard to the rotor branch RZ on the first embodiment, in particular in that in the first embodiment, the fifth embodiment, in the sixth embodiment, the first fluid flowing through the rotor 16 on its way from the rotor 16 to and into the reservoir 34 does not flow through the gear 38, thus that the, in particular the entire, first fluid flowing through the rotor 16 is to be guided from the rotor 16 into the reservoir 34, bypassing the gear 38. In contrast, the Fig. The seventh embodiment shown in Figure 7, for example, is based on the second embodiment. The stator branch SZ and the rotor branch RZ are joined at the junction point ZS, which coincides with the branching point VZ at which the return line 36 branches into the branches Z1 and Z2, particularly with regard to a flow of the first fluid away from the part 22 and toward the reservoir 34, which is the case, for example, in the first operating state or in the switching state S3 of the valve V1. In particular, the seventh embodiment is based on the fourth embodiment, but with the difference that instead of the valve V2, the valve V8 is arranged in the rotor branch RZ and upstream of the rotor 16 and downstream of the branching point AS.

[0082] The Fig. The eighth embodiment shown in Figure 8 is based on the first embodiment. Here, in the flow direction of the first fluid flowing through the circuit 20 and thus conveyed through the circuit 20, for example, by means of the pump 32, the heat exchanger 26 is arranged downstream of the pump 32 and upstream of the part 22, and the heat exchanger 30 is arranged downstream of the part 22 and upstream of the pump 32. In the eighth embodiment, the valve V7 provided, for example, in the fifth embodiment is provided.

[0083] The Fig. The ninth embodiment shown in Figure 9 is essentially a combination of the seventh embodiment and the eighth embodiment. As in the eighth embodiment, the first fluid flowing through the rotor 16 and thus the rotor branch RZ bypasses the gear 38 on its way from the rotor 16 to and into the reservoir 34. As in the third embodiment, the return line 36 branches into branches Z1 and Z2 at the branching point VZ, which coincides with the connection point VS2, with branch Z1 leading from the branching point VZ to the valve V1. The gear 38 is arranged in the branch Z2 upstream of the reservoir 34 and downstream of the branching point VZ. However, the valve V3 is not provided in the ninth embodiment.The heat exchanger 30 is arranged in the branch Z1 such that, relative to the switching state S3 of the valve V1 and thus relative to a flow of the first fluid from the branching point VZ to the valve V1, the heat exchanger 30 is arranged downstream of the branching point VZ and thus downstream of the stator 14 and upstream of the valve V1. In the rotor branch RZ, in the ninth embodiment, the valve V8 is arranged instead of the valve V2.

[0084] In a sixteenth embodiment not shown in the figures, it is provided, for example, that the sixteenth embodiment is designed like the ninth embodiment, with the only differences being that valve V2 is provided instead of valve V8 and valve V3 is arranged in branch Z2 upstream of the transmission 38 and in particular downstream of the branching point VZ. In a seventeenth embodiment not shown in the figures, it is provided, for example, that the seventeenth embodiment is designed like the sixteenth embodiment, in particular with the only difference that valve V2 is omitted, in particular without replacement.In an eighteenth embodiment not shown in the figures, it can be provided, for example, that the eighteenth embodiment is designed like the ninth embodiment, in particular with the only difference that the valve V3 is arranged in the branch Z2 upstream of the transmission 38 and downstream of the branching point VZ.

[0085] The Fig. The tenth embodiment shown in Figure 10 is essentially a combination of the ninth embodiment and the seventh embodiment, since in the tenth embodiment the stator branch SZ and the rotor branch RZ are joined at the junction point ZS, which coincides with the branching point VZ, at which the return line 36 branches into the branches Z1 and Z2. It can be seen that, in comparison to the ninth embodiment, in the tenth embodiment the valve V3 is arranged in the branch Z2 upstream of the transmission 38 and downstream of the junction point ZS. As in the ninth embodiment, the heat exchanger 30 is arranged in the branch Z1 such that the heat exchanger 30 is arranged downstream of the junction point ZS and upstream of the valve V1 with respect to a flow of the first fluid running from the junction point ZS to the valve V1.

[0086] At the Fig. In the eleventh embodiment shown in Figure 11, the valve V7 is omitted, so that, for example, as in the third embodiment, the valve V6 is arranged in the circuit 28 instead of the valve V7.

[0087] The Fig. The twelfth embodiment shown in Figure 12 essentially corresponds to the eighth embodiment. It can be seen that, for example, a second check valve RV2 is arranged in the third circuit 28.

Claims

[1] Electric drive device (10) for a motor vehicle, with at least one electric machine (12) by means of which the motor vehicle can be driven, with a first circuit (20) through which a lubricant and / or coolant can flow as the first fluid, with a second circuit (24) through which a cooling fluid different from the first fluid can flow as the second fluid, and with a first heat exchanger (26) arranged both in the first circuit (20) and in the second circuit (24), via which heat can be exchanged between the first fluid and the second fluid, with: - a refrigerant circuit (28) through which the first fluid and the second fluid can flow as the third fluid; and - a second heat exchanger (30) arranged both in the first circuit (20) and in the third circuit (28), via which heat can be exchanged between the first fluid and the third fluid, wherein at least a part (22) of the electric machine (12) is arranged in the first circuit (20) such that the part (20) is to be lubricated and / or cooled by means of the first fluid, a battery (18), a vehicle radiator (46) and power electronics (50) are arranged in the second circuit (24), and the third refrigerant circuit (28) is designed to bring about targeted changes in the state of aggregation of the third fluid. [2] Electric drive device (10) according to claim 1, characterized by that a pump (32) is arranged in the first circuit (20), by means of which the first fluid can be conveyed through the first circuit (20). [3] Electric drive device (10) according to claims 1 and 2, characterized bythat the first heat exchanger (26) is arranged downstream of the pump (32) and upstream of the part (22) in the first circuit (20). [4] Electric drive device (10) according to claims 1 and 2 or according to claim 3, characterized by that the second heat exchanger (30) is arranged downstream of the part (22) and upstream of the pump (32) in the first circuit (20). [5] Electric drive device (10) according to claim 4, characterized by in that the second heat exchanger (30) is arranged in the first circuit (20) downstream of the part (22) and upstream of a reservoir (34) arranged in the first circuit (20), in which reservoir the first fluid can be received to form a sump, wherein the pump (32) is arranged upstream of the first heat exchanger (26) and downstream of the reservoir (34) in the first circuit (20). [6] Electric drive device (10) according to one of the preceding claims, characterized by , that: - the part (22) comprises a rotor (16) of the electrical machine (12) and a stator (14) of the electrical machine (12); and - the first circuit (20) branches into a rotor branch (RZ), in which the rotor (16) is arranged, and a stator branch (SZ) connected in parallel to the rotor branch (RZ), in which the stator (14) is arranged. [7] Electric drive device (10) according to claim 6, characterized by , that: - the first circuit (20) branches at a branching point (AS) into the rotor branch (RZ) and the stator branch (SZ); and - a valve element (V2) is arranged downstream of the branching point (AS) and upstream of the rotor (14) in the rotor branch (RZ), by means of which valve element a quantity of the first fluid flowing through the rotor branch (RZ) can be adjusted. [8] Motor vehicle, with at least one electric drive device (10) according to one of the preceding claims. [9] Method for operating an electric drive device (10) according to one of claims 1 to 7.

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