Device and method for distributing a cooling / lubricating oil flow on designal in an electrical traction

Abstract

The invention relates to a device (1) for distributing a cooling / lubricating oil flow as required in an electric traction drive, comprising an electrically controllable motor-pump unit (2) and a hydraulic device (19), the motor-pump unit (2) being actuatable in two directions of rotation, and the motor-pump unit (2) being connected to the hydraulic device (19) by means of a heat exchanger (5) with a hydraulic device (19) for a partial volume flow (10, 11). 10 ', 10' ', 10 '''), which are connected at least to the stator of the electric machine and / or to the rotor of the electric machine and / or to the transmission for cooling and / or heating and / or lubrication, at least one fluid outlet being additionally opened via at least one hydraulically switchable valve when the motor-pump unit (2) is reversed in direction of rotation.

Description

Technical Field

[0001] The present invention relates to a device and a method for distributing a cooling oil flow / lubricating oil flow as needed in an electric traction drive device, the device having an electrically controllable motor-pump unit and a hydraulic device, wherein the motor-pump unit can be operated in two rotational directions, and wherein the motor-pump unit is connected via a heat exchanger to a plurality of fluid outlets, which are connected at least to the stator of the electric machine, the rotor of the electric machine, and the transmission for cooling and / or heating and / or lubricating. Background Art

[0002] Oil-cooled electric machines are partially or completely used in powerful electric drive devices with high energy density. Here, the rotor shaft and / or the stator of the electric machine are cooled with oil. In a completely oil-cooled electric machine, the cooling oil requirements of the rotor shaft and the stator - depending on the respective operating point - vary in particular due to the copper losses, iron losses, and electromagnetic losses occurring in the electric machine. Therefore, for maximum high thermal availability and minimization of the loss power, it is necessary to distribute the sub-volume flows to the rotor shaft and the stator as needed.

[0003] Known solutions use passive, pressure-controlled, or temperature-controlled valves, as described in DE102017101826A1. The use of active, electrically controllable switching valves or proportional valves is likewise possible, but is mostly avoided for cost reasons.

[0004] When using passive, pressure-controlled, or temperature-controlled valves, the disadvantages are the influence of manufacturing tolerances and component tolerances and the usually large hysteresis in the working area. An active influence on the switching characteristics is not possible or only limitedly possible. Such an influence of a pressure-controlled valve, for example, can be achieved by a short-term increase or decrease in the rotational speed of the pump motor, but this also affects the delivered volume flow. Sensitive adjustability is generally not possible, rather discrete switching valve characteristics are achieved thereby.

[0005] The use of active, electrically controllable switching valves or regulating valves is associated with high costs for the valves and the electrical integration and is generally avoided for cost reasons.

[0006] Typically, an oil pump driven by a brushless DC motor (BLDC motor) is used, which provides a delivery volume flow that can be set as needed via the rotational speed adjustment of the BLDC motor independently of the vehicle speed. As a preferred pump type, a rotary displacement pump is used in embodiments such as a toothed ring pump or a cycloidal rotor pump. A cycloidal rotor pump consists of a wheel set with an inner rotor and an outer rotor, and a pump housing that is typically implemented in two parts or three parts. However, this simple and proven implementation itself brings high costs for the motor-pump unit, especially for the BLDC motor and the required commutation electronics such as a BLDC driver for motor control or a B6 bridge circuit.

[0007] DE 10 2017 113 057 A1 relates to a coolant delivery module for a transmission, preferably an automatic transmission.

[0008] There are motor-pump units that can be electrically controlled, but the motor-pump units cannot be operated in both rotational directions. There is a connection via a heat exchanger. However, a partial flow is not used for cooling or heating or lubricating the stator of the electric machine. The partial flow is also not used for cooling the rotor.

[0009] This prior art relates to a solution with a costly valve structure.

[0010] Document DE 10 2019 100 872 A1 studies the cooling and lubrication of an electric hybrid drive device via a fluid outlet.

[0011] In the first rotational direction of the pump, the heat exchanger is supplied with fluid via a pipeline, and the fluid then performs all cooling and lubrication tasks via appropriate pipelines.

[0012] In the second delivery direction, pressure is applied to either the clutch or the parking lock via pipeline 1.

[0013] Although the document uses a motor that can reverse its rotational direction and perform different tasks in both rotational directions. However, the implementation is very complex.

[0014] Document DE 32 10 759 A1 studies volume regulation via a pump with multiple pump stages or multiple pumps. It cannot be derived from this document that the sub-volume flow to the stator or the winding head includes the largest share of the volume flow.

[0015] Document DE 10 2018 007462A1 describes a solution with a pump having two pump outlets, where the outlets are used for cooling and lubricating the transmission.

[0016] DE 10 2009 038 377 A1 shows a hydraulic device for controlling multiple clutches, which has an adjustable torque distribution device. There is a high-pressure partial circuit of an accumulator for operating the clutches by means of associated switchable valves. The oil cooling of the clutches is carried out on the low-pressure side, where the switchable valve controls the oil flow by means of a clock.

[0017] DE 102013224667 A1 shows a hydraulic device with an adjustable valve, such that it can be adjusted in different operating modes with different operating principles or adjustment parameters.

[0018] The object of the present invention is to achieve a functional added value by means of the second rotational direction of a motor-pump unit via an additional simple hydraulic shut-off valve, and to be able to provide, as required, a cooling oil flow to the rotor shaft and stator of an electric machine.

[0019] Here, compared with the known prior art, the costs should not increase or only increase minimally and at the same time an equivalent or improved control of the sub-volume flow should be achieved. Summary of the Invention

[0020] The object is achieved by means of a device for distributing a cooling oil flow / lubricating oil flow as required in an electric traction drive device, the device having an electrically controllable motor-pump unit and a hydraulic device, wherein the motor-pump unit can be operated in two rotational directions, and wherein the motor-pump unit is connected via a heat exchanger to a plurality of fluid outlets, which are connected at least to the stator of the electric machine and / or the rotor of the electric machine and the transmission for cooling and / or heating and / or lubricating, wherein when the rotational direction of the motor-pump unit is reversed, at least one fluid outlet is additionally opened via at least one hydraulically switchable valve.

[0021] The device according to the invention is largely independent of the motor-pump unit used. Only a slot-controlled positive-displacement pump and a motor that can operate bidirectionally are required. The positive-displacement pump is configured as an axial piston pump, a radial piston pump, a vane pump, a roller vane pump or a cycloid rotor pump. All of these pumps are regularly slot-controlled, i.e., they have a suction slot on the suction side and a pressure slot on the pressure side, and the use of the suction slot ensures good suction capacity. The slot control device enables a simple construction of the pump.

[0022] The motor-pump unit present on the system side is extended with simple and cost-effective hydraulic valves, non-return valves, so that bidirectional operation of the pump is feasible. Thereby, different - fixedly defined via hydraulic resistance control - volume flow distributions are achieved with clockwise and counterclockwise rotation of the pump. In addition, by means of intermittent commutation operation, any distribution is achieved at the fluid outlet that is within a fixed division on average over time. This is achieved purely in software by correspondingly modulating the rotational speed and cycle duration in the clockwise and counterclockwise rotation of the motor-pump unit.

[0023] Therefore, compared with the use of electrically actuated switching valves or proportional valves, a cost advantage can be achieved with the solution according to the invention. Compared with the use of passively actuated, thermally controlled or pressure-controlled valves, a functional added value can be achieved by precisely and comprehensively controlling the sub-volume flow due to the elimination of tolerances and hysteresis effects.

[0024] Advantageously, a sub-volume flow is provided for the electric traction drive via the fluid outlet, wherein the sub-volume flow to the stator or the winding head of the stator comprises the largest share of the volume flow.

[0025] The presetting of the sub-volume flow can be achieved via a baffle.

[0026] The hydraulically switchable valve is a hydraulically unlockable non-return valve or a hydraulically actuated two-way valve or a hydraulically controlled proportional valve.

[0027] The hydraulic device is constructed via a plurality of housing plates, wherein each housing plate bears at least one functional unit.

[0028] The functional unit comprises at least one valve of the valves and / or radially arranged holes leading into a surrounding annular groove.

[0029] The object is also achieved by a method for distributing a cooling oil flow / lubricating oil flow as required in an electric traction drive, the electric traction drive having an electrically controllable motor-pump unit and a hydraulic device, wherein the motor-pump unit is controlled in two rotational directions, and wherein the motor-pump unit is connected via a heat exchanger to a plurality of fluid outlets, which are connected at least to the stator of the electric machine, the rotor of the electric machine and the transmission for cooling and / or heating and / or lubricating, wherein when the rotational direction of the motor-pump unit is reversed, at least one fluid outlet is additionally opened via at least one hydraulically switchable valve.

[0030] Advantageously, different operating modes are set in order to set the flow rate of the corresponding sub-volume flow at the fluid outlet, wherein in the operating mode in commutation operation, switching is carried out between the rotational directions of the motor-pump unit in a time clock-controlled manner.

[0031] Here, different operating modes of the motor-pump unit for operation or reverse operation in the rotational direction A or rotational direction B can be set.

[0032] Set additional speed-related control of the motor-pump unit.

[0033] The following advantages result from the solution according to the invention:

[0034] The present invention allows the control of the sub-volume flow as required to improve the efficiency and / or thermal availability of an electric drive system with an electric machine that is fully or partially oil-cooled.

[0035] Hydraulically actuated valves allow precise control of the sub-volume flow without additional electrical energy requirements.

[0036] The solution is largely independent of the motor-pump unit used and is compatible with existing motor components and pump components.

[0037] The setting can be achieved in a robust structural manner by using simple hydraulic shut-off valves and intelligent operating strategies.

[0038] High flexibility is provided by the feasibility of adjusting the sub-volume flow in software terms.

[0039] By combination with intelligent self-learning function software, the desired maximum values in terms of efficiency and / or thermal availability can be achieved - depending on the operating state.

[0040] Since the hydraulic valve can be fully integrated in the area of the pump head, for example by the shown housing plate structure, very good compatibility with the platform concept or with the provisions for using common components results. Description of the Drawings

[0041] Figure 1 Hydraulic circuit diagram showing a first embodiment of a device with a shut-off valve,

[0042] Figure 2 Showing the operating modes achievable with the first embodiment,

[0043] Figure 3 Exemplarily showing a qualitative curve of the volume flow,

[0044] Figure 4 Hydraulic circuit diagram showing a second embodiment of the shut-off valve device,

[0045] Figure 5 Hydraulic circuit diagram showing a third embodiment of the shut-off valve device,

[0046] Figure 6 Hydraulic circuit diagram showing a fourth embodiment of the shut-off valve device,

[0047] Figure 7 A hydraulic circuit diagram showing another embodiment for distributing cooling oil flow / lubricating oil flow as required

[0048] Figure 8 Showing an operating mode that can be achieved by means of the device shown in Figure 7

[0049] Figure 9 A qualitative diagram showing variables related to the reversal of the rotation direction during the commutation process

[0050] Figure 10 Exemplarily showing a method for distributing cooling oil flow / lubricating oil flow as required in an electric traction drive device

[0051] Figure 11 Showing an isometric view of an embodiment of the device shown in Figure 1

[0052] Figure 12 Showing another isometric view of the embodiment according to Figure 11

[0053] Figure 13 Showing an end view of the embodiment according to Figure 11 and Figure 12

[0054] Figure 14 Showing the corresponding negative image geometry of the embodiment shown in Figures 11 to 13 to illustrate the hydraulic flow path

[0055] Figure 15 Showing an isometric view of a second embodiment of the device shown in Figure 1

[0056] Figure 16 Showing Figure 15 the end view of

[0057] Figure 17 Showing a side view of the embodiment shown in Figure 15

[0058] Figure 18 Showing a cross-sectional view along the cutting plane A-A shown in Figure 16

[0059] Figure 19 Showing a cross-sectional view along the cutting plane B-B shown in Figure 17

[0060] Figure 20 Showing Figure 15 the isometric view of​​​​​​​​

[0061] Figure 21 Shows an isometric view of the first housing plate,

[0062] Figure 22 Shows an isometric view of the pivotable flap valve,

[0063] Figure 23 Shows an isometric view of the first housing plate,

[0064] Figure 24 Shows an isometric view of the first housing plate. Detailed Description

[0065] Figure 1 Shows a hydraulic circuit diagram according to device 1 for controlling a sub-volume flow 10 as required, the device having a shut-off valve device in a first embodiment.

[0066] The coolant lubrication pump 4 is driven by an electric motor 3 which can rotate in two rotational directions. These two components form an electrically controllable motor-pump unit 2.

[0067] The coolant lubrication pump 4 is connected to the oil sump 15 via a first check valve 6' and a second check valve 6'' on the suction side and the pressure side. Depending on the rotational direction of the pump, one of these two check valves 6', 6'' is in the open position while the respective other check valve is in the closed position. The connection to the oil sump is effected by means of a sieve or filter element 16 arranged therebetween.

[0068] Here, the entire delivery volume flow provided by the pump 3 always passes via the switching valve 7 and the heat exchanger 5. The hydraulically controlled shut-off valve 8 is in the closed position in the rotational direction A. Thus, the entire delivery volume flow is divided at the respective fluid outlets between the stator WH, 12 and the transmission GBX, 13. Specifically, the division of the sub-volume flows 10'' and 10''' to the fluid outlets is effected via a baffle 14''' arranged in the inflow to the transmission.

[0069] In the rotational direction B, the hydraulically controlled shut-off valve 8 is unlocked via the pump pressure applied in the control line 9. Thus, the entire delivery volume flow is divided between the rotor RS, 11, the stator WH, 12 and the transmission GBX, 13. The desired division of the sub-volume flows 10'', 10''' - similar to the operation in the first rotational direction A - is effected via another baffle 14' arranged in the inflow to the rotor 11.

[0070] By means of intermittent commutation operation, it is possible to arbitrarily divide the volume flow into sub-volume flows within a fixedly defined distribution of clockwise and counterclockwise operation of the motor-pump unit.

[0071] In each operating mode 26, the numerically largest partial volume flow 12 is directed directly and without additional throttling to the stator WH, 12. This enables an energy-efficient distribution of the remaining, numerically smaller partial volume flows 11, 13 via hydraulic resistance control. Preferably, the hydraulic resistance control is achieved by means of an orifice plate with a defined flow cross-section. Thereby, a largely viscosity-independent and thus temperature-independent division of the partial volume flows 10', 10'' can be achieved.

[0072] The control is effected via an electronic control unit 21, which is connected to a data bus 22. The control unit 21 is connected via an electrical line 20 to the motor 3 of the motor-pump unit 2.

[0073] Figure 2 Shows the operating mode 26 that can be achieved with the device shown in Figure 1 and an exemplary volume flow division for the first rotational direction 27, i.e., rotational direction A, the second rotational direction 28, i.e., rotational direction B, and the reversing operation 29 of the motor-pump unit 2. The divisions shown each relate to the entire delivery volume flow provided by the pump 3.

[0074] For two operating states with different requirements for the cooling oil demand, e.g., for an operating point with a high driving torque or for an operating point with a high rotational speed, a nominal design for the division of the partial volume flow in the rotational direction A and in the rotational direction B is determined. The nominal design is carried out such that for most operating points, a good division is given in the first rotational direction 27, i.e., rotational direction A, or in the second rotational direction 28, i.e., rotational direction B. In addition, any intermediate distribution can be achieved by the alternating operation of the motor-pump unit in the rotational direction A and in the rotational direction B, i.e., the so-called reversing operation 29.

[0075] Figure 3 Exemplarily shows the qualitative course over time of the flow rate of the controllable partial volume flow 10 during intermittent reversing operation by modulating the rotational speed in the first rotational direction 27, in the second rotational direction 28, and the underlying cycle duration 35. The volume flows Q A and Q B can be modulated arbitrarily on the time axis.

[0076] Due to the inertia given by the thermal mass of the thermal process, the influence of the cycle duration 35 can be almost neglected, and a time-averaged constant partial volume flow 10', 10'' results.

[0077] Figure 4 Shows the hydraulic circuit diagram of a second embodiment of the device 1 with a motor-pump unit 2 and a shut-off valve device. Here, the hydraulically controllable switching valve 24 is implemented by a two-way two-position valve, in this embodiment a poppet valve.

[0078] Figure 5 The hydraulic circuit diagram of the third embodiment of the device 1 with the motor-pump unit 2 and the shut-off valve arrangement is shown. Here, the hydraulic shut-off valve is implemented by a hydraulically controlled 2 / 2-way proportional valve. Figure 1 and Figure 4 The embodiment shown in makes it possible to influence the distribution of the partial volume flows additionally via the control pressure and thus via the pump speed of the pump 4 .

[0079] Figure 6 The hydraulic circuit diagram of a fourth embodiment of the device 1 with a motor-pump unit 2 and a shut-off valve arrangement is shown. Additional control lines and hydraulically controlled shut-off valves with the aid of a control piston 17 can be omitted here. The entire delivery flow is again routed via the heat exchanger 5. The heat exchanger is connected to the respective suction and pressure sides of the pump 3 via a first switching valve 7' and a second switching valve 7", respectively. In contrast to the previous embodiments, the heat exchanger 5 flows in different directions in the two rotational directions of the pump. For example, the volume flow delivered by the pump flows through the heat exchanger in countercurrent in the first rotational direction A and in cocurrent in the second rotational direction B.

[0080] Figure 7 The hydraulic circuit diagram of another embodiment for distributing the cooling oil flow / lubricating oil flow as required is shown. In this case, two additional hydraulically controlled proportional valves 25 ′ and 25 ″ are used to expand the range of functions.

[0081] The uncooled partial volume flow is supplied to the transmission via the hydraulically controlled proportional valve 25' of the control line 9. As a result, the transmission oil sump temperature can be increased quickly, especially in the cold state, and the efficiency can be increased.

[0082] The remaining volume flow of the pump passes through the heat exchanger and is divided via further proportional valves, each of which is actuated via a hydraulic control line 9 .

[0083] The partial volume flow 11 is likewise conducted to the transmission via a proportional valve 25 ′, where it is used for cooling. The partial volume flow 13 is conducted to the rotor shaft via a proportional valve 25 ′″.

[0084] Figure 8 Show that you can use Figure 7 The arrangement shown in FIG. 1 realizes an operating mode 26 and an associated valve position 30 of the hydraulically controlled proportional valves 25 ′, 25 ″ and 25 ′″.

[0085] Figure 9 A qualitative diagram of variables that are inversely dependent on the direction of rotation during a commutation process is shown, specifically the rotation angle 31 s(t), the angular velocity 32 , v(t) and the angular acceleration 33 , a(t) are plotted against the time t.

[0086] Figure 10 An exemplary method for distributing a cooling oil flow / lubricating oil flow as required in an electric traction drive device having a device according to the invention according to one of the above-mentioned figures is shown. Here, a distinction is made between a speed-regulated operation in a first rotational direction A or a second rotational direction B and an intermittent commutation operation in rotational directions A and B.

[0087] In the flow chart, it is first queried whether the vehicle is in motion. If the answer to this question is yes, a check of the torque is carried out. If there is a high torque or a high torque is to be set, it is queried whether the limit temperature at the stator or the stator winding WH is reached.

[0088] If the limit temperature is reached, it is queried whether the limit temperature of the rotor RS of the electric machine is reached. If this is not the case, a speed-regulated pump operation is set in the rotational direction A. If both limit temperatures are reached or exceeded, a reduced performance operation is set.

[0089] In the case where the vehicle is in motion, a high speed can also be requested. Here, the limit temperature is also queried again, where first the limit temperature of the electric machine is queried and then the limit temperature of the stator winding is queried. If the temperature is within a predetermined range, a speed-regulated operation in the rotational direction B is started here.

[0090] If the limit temperature is still below the threshold value respectively when querying the limit temperature, a commutation operation with a speed duration modulated according to the operating strategy is called not only in the branch of the high torque request but also in the branch of the high speed request.

[0091] If the vehicle at rest is to be actively air-conditioned, a speed-regulated pump operation in the rotational direction A is immediately set.

[0092] Figure 11 Shown in Figure 1 is an isometric view of an embodiment of the device 1 for distributing a cooling oil flow / lubricating oil flow as required as shown in. In Figure 11 and Figure 12 a motor-pump unit 2 which can be electrically controlled is shown on the right, which motor-pump unit consists of an electric motor 3 and a cooling lubricating oil pump 4. An electrical connector 23 enables an electrical connection.

[0093] The housing of the hydraulic component consists of housing plates 40', 40", 40"' and is constructed in a multi-piece manner. The individual housing plates 40', 40", 40"' are screwed to one another via bolts 45 and the associated mating sleeves 44.

[0094] With a multi-piece housing embodiment having housing plates fixed relative to one another via a mating sleeve 44 and bolts 45, cost-effective manufacturing and installation as well as good industrial feasibility can be achieved. Here, the housing plates are embodied as sintered parts or plastic injection-molded parts.

[0095] Optionally, the connection of the housing plates 40', 40'', 40''' can be achieved by other form-fitting, friction-fitting or material-fitting connection techniques, specifically by hooks, clamping, pressing, bonding or welding. In addition, the connection of the housing plates 40', 40'', 40''' via bayonet-type connectors is feasible.

[0096] The corresponding sub-volume flows 10', 10'', 10''' are guided outwards via holes 41 which are radially arranged and lead into the surrounding annular grooves 42', 42'', 42'''. The seal between the annular grooves is achieved via an O-ring 43. To avoid internal oil leakage flows, the housing plates 40', 40'' and 40''' can optionally be sealed relative to one another via paper seals or other soft-sealed sealing elements. In the case of sintered parts embodied with end faces having surface grinding, additional seals can be dispensed with.

[0097] Figure 13 With regard to the housing plate 40' together with two check valves 6', 6'' shown according to Figure 11 and Figure 12 shows an end-side view of an embodiment. The switching valve 7 and the hydraulically controllable shut-off valve 8 are also installed in the housing plate 40'.

[0098] Figure 14 Shown in Figures 11 to 13 the corresponding negative-image geometry 18 in the embodiment shown in to illustrate the hydraulic flow path. The two check valves 6', 6'' as well as the switching valve 7 and the hydraulically controllable shut-off valve 8 together with their control pistons 17 are shown again.

[0099] Figure 15 Shown in Figure 1 is an isometric view of a second embodiment of a device for distributing a cooling oil flow / lubricating oil flow as required, having a two-piece housing embodiment.

[0100] On the right side of Figure 15 is shown an electrically controllable motor-pump unit 2, which consists of an electric motor 3 and a cooling lubricant pump 4. The electrical connector 23 enables an electrical connection. The housing of the hydraulic components is composed of the housing plates 40', 40'', 40''' and is constructed in a multi-piece manner. The individual housing plates 40', 40'', 40''' are screwed to one another via bolts 45 and the associated mating sleeves 44.

[0101] Alternatively, the housing plates 40 ′, 40 ″, 40 ′″ can be connected by other form-fitting, friction-fitting or material-fitting connection techniques, in particular by hooking, clamping, pressing, bonding or welding. Furthermore, the connection of the housing plates 40 ′, 40 ″, 40 ′″ via a bayonet connection is possible.

[0102] The respective partial volume flows 10 ′, 10 ″, 10 ′″ are guided outward via radially arranged holes 41 that open into circumferential annular grooves 42 ′, 42 ″, 42 ′″. The sealing between the annular grooves is achieved via O-rings 43. To prevent internal oil leakage relative to one another, the housing plates 40 ′, 40 ″, 40 ′″ can optionally be sealed via paper seals or other soft-sealing sealing elements. In the case of a sintered component with surface-ground end faces, additional sealing can be dispensed with.

[0103] The suction is effected—depending on the direction of rotation of the electric motor 3 —in each case via an inlet valve 50 ′ or 50 ″ arranged downstream of the filter screen 16 integrated at the end.

[0104] Figure 16 Focusing on the filter screen 16 and the two inlet valves 50' and 50" shown in Figure 15 FIG. 1 is an end view of an embodiment for distributing cooling oil flow / lubricating oil flow as needed.

[0105] Figure 17 Shown in Figure 15 1 is a side view of an embodiment for distributing cooling oil flow / lubricating oil flow as needed.

[0106] Figure 18 Shown along the Figure 16 sectional view of the section plane AA shown in FIG. The cut-off valve 8 can be seen in the sectional view. The cut-off valve is constructed by means of a control piston 65 with a valve spring 67 and a cut-off function 66 and is closed by an end cap 68.

[0107] Figure 19 Shown along the Figure 17 Here, the switching valve 7 is designed as a pivot flap valve 51 in a valve housing 58 .

[0108] Figure 20 Shown in Figure 15 An isometric view of an embodiment for distributing the cooling oil flow / lubricating oil flow as required is shown in the figure, in which the second housing plate 40 is omitted. In this figure, in addition to the inlet valves 50', 50", the switching valve 7 implemented as a pivoting flap valve 51 in the valve housing 58 and the shut-off valve 8 that can be hydraulically actuated via the control piston 65 can be seen.

[0109] Figure 21 An isometric view of the first housing plate 40' for accommodating the switching valve 7 is shown. Symmetrically to the outlet opening 61 of the switching valve 7, sealing surfaces 59 are provided on both sides in a wedge shape, which have an extension along the longitudinal axis of the device 1. The sealing surfaces 59 taper towards the support housing 60 for guiding the support pin 53. The support housing 60 defines the associated pivot axis 52. By means of the embodiment of the pivot flap valve 51 according to the invention, the pivot flap valve can be supported via the support housing 60 and the functionally related sealing surfaces 59 on only one housing part, namely the valve housing 58. Thereby, the influence of manufacturing tolerances can be kept small.

[0110] Figure 22 An isometric view of the components of the switching valve 7 embodied as a pivot flap valve 51 is shown, which has sealing surfaces 54 provided on both sides, which can bear against the sealing surfaces 59 of the valve housing 58. The switching valve 7 is guided in the region of the support pin 53 and can pivot about the pivot axis 52. The component is embodied as a wedge-shaped component with a circumferential circular section 62.

[0111] Dirt collecting grooves 55 provided at the outer circumferential circular section 62 and in the region of the support pin 53 can achieve the accommodation of dirt particles entering the region of the support and sealing sites, and thereby reduce the risk of jamming. Connecting holes 56 provided in the axial direction and pressure relief grooves 57 introduced on at least one side of the pivot flap valve 51 can achieve pressure equalization between the end sides of the pivot flap valve 51 and the outlet opening 61 provided in the first housing plate 40'.

[0112] Figure 23 An isometric view of the first housing plate 40' with the pivot flap valve 51 according to the invention in the first angular position Φ1 is shown.

[0113] Figure 24 An isometric view of the first housing plate 40' with the pivot flap valve 51 according to the invention in the second angular position Φ2 is shown.

[0114] List of reference numerals

[0115] 1 Device for controlling the sub-volume flow as required

[0116] 2 Electrically controllable motor-pump unit

[0117] 3 Electric motor

[0118] 4 Cooling lubricant pump

[0119] 5 Heat exchanger

[0120] 6 Check valve

[0121] 6’ First check valve

[0122] 6” Second check valve

[0123] 7 Changeover valve

[0124] 7’ First changeover valve

[0125] 7” Second changeover valve

[0126] 8 Hydraulically controllable shut-off valve

[0127] 9 Hydraulic control line

[0128] 10 Sub-volume flow

[0129] 10’ First sub-volume flow

[0130] 10” Second sub-volume flow

[0131] 10”’ Third sub-volume flow

[0132] 11 Sub-volume flow to rotor / to rotor shaft

[0133] 12 Sub-volume flow to stator / to winding head

[0134] 13 Sub-volume flow to transmission

[0135] 14 14’14”14”’ Baffle

[0136] 15 Oil sump

[0137] 16 Screen / filter element

[0138] 17 Control piston

[0139] 18 Negative image geometry of flow path

[0140] 20 Electrical circuit

[0141] 21 Electrical control unit

[0142] 22 Data bus

[0143] 23 Connector

[0144] 24 Hydraulically controllable switching valve

[0145] 25 25’25”25”’ Hydraulically controllable proportional valve

[0146] 26 Operating mode

[0147] 27 First rotation direction or rotation direction A

[0148] 28 Second rotation direction or rotation direction B

[0149] 29 Reversing operation

[0150] 30 Valve position

[0151] 31 Rotation angle

[0152] 32 Angular velocity

[0153] 33 Angular acceleration

[0154] 34 Impact

[0155] 35 Period duration

[0156] 40, 40’, 40”, 40”’ Housing plate

[0157] 41 Outlet hole

[0158] 42, 42’, 42”, 42”’ Annular groove

[0159] 43 O-ring

[0160] 44 Fitting sleeve

[0161] 45 Bolt

[0162] 50 Inlet valve

[0163] 50’ First inlet valve

[0164] 50” Second inlet valve

[0165] 51 Pivoting flap valve

[0166] 52 Pivot axis

[0167] 53 Support pin

[0168] 54 Sealing surface

[0169] 55 Dirt collection trough

[0170] 56 Connection hole

[0171] 57 Pressure relief groove

[0172] 58 Valve housing

[0173] 59 Sealing surface

[0174] 60 Support housing

[0175] 61 Outlet opening

[0176] 62 Circular part circumferential

[0177] 65 Control piston

[0178] 66 Stop valve

[0179] 67 Valve spring

[0180] 68 End cover

[0181] Φ1 First angular position

[0182] Φ2 Second angular position

Claims

1. A device (1) for distributing a cooling oil flow / lubricating oil flow as required in an electric traction drive device, the device having an electrically controllable motor - pump unit (2) and a hydraulic device (1), wherein the motor - pump unit (2) can be operated in two rotational directions, and wherein the motor - pump unit (2) is connected via a heat exchanger (5) to a plurality of fluid outlets for sub - volume flows (10, 10’, 10”, 10”’), the fluid outlets being connected at least to the stator of the electric machine and / or the rotor of the electric machine and / or the transmission for cooling and / or heating and / or lubricating, wherein when the motor - pump unit (2) reverses its rotational direction, at least one fluid outlet is additionally opened via at least one hydraulically switchable valve.

2. The device (1) according to claim 1, characterized in that, A sub - volume flow (10) is provided for the electric traction drive device via the fluid outlet, wherein the sub - volume flow (12, 10’) to the stator or the winding head of the stator comprises the largest share of the volume flow.

3. The device (1) according to claim 1 or 2, characterized in that, The sub - volume flows (10, 10’, 10”, 10”’) are preset via baffles.

4. The device (1) according to any one of the preceding claims, characterized in that, The hydraulically switchable valve is a hydraulically controllable shut - off valve (8) or a hydraulically controllable proportional valve (25) or a hydraulically controllable switching valve (24).

5. The device (1) according to any one of the preceding claims, characterized in that, At least one conversion valve (7) connects the corresponding suction side and pressure side of the pump (3).

6. The device (1) according to claim 5, characterized in that, The conversion valve (7) is a pivoting flap valve (51).

7. The device (1) according to any one of the preceding claims, characterized in that, The hydraulic device (19) is constructed via a plurality of housing plates (40, 40’, 40”, 40”’), wherein the housing plates (40, 40’, 40”, 40”’) each carry at least one functional unit.

8. The device (1) according to claim 7, characterized in that, The housing plates (40, 40’, 40”, 40”’) are screwed to each other and to the cooling and lubricating oil pump (3).

9. The device (1) according to claim 7 or 8, characterized in that, The functional unit includes at least one of the valves and / or radially arranged holes (41) leading into surrounding annular grooves (42’, 42”, 42”’).

10. A method for distributing a cooling oil flow / lubricating oil flow as required in an electric traction drive device, the device having an electrically controllable motor - pump unit (2) and a hydraulic device (1), wherein the motor - pump unit (2) can be operated in two rotational directions, and wherein the motor - pump unit (2) is connected via a heat exchanger (5) to a plurality of fluid outlets, the fluid outlets being connected at least to the stator of the electric machine and / or the rotor of the electric machine and / or the transmission for cooling and / or heating and / or lubricating, wherein when the motor - pump unit (2) reverses its rotational direction, at least one fluid outlet is additionally opened via at least one hydraulically switchable valve.

11. The method according to claim 10, wherein Different operating modes are set, and the flow rates of the corresponding sub - volume flows (10, 10’, 10”, 10”’) at the fluid outlets are set, wherein in the operating mode during commutation operation, the rotational directions of the motor - pump unit (2) are periodically switched in time between each other.

12. The method according to claim 10 or 11, characterized in that, Different operating modes can be set during the operation of the motor - pump unit (2) in rotational direction A or rotational direction B or during commutation operation.

13. The method according to claim 12, characterized in that, There is an additional control of the motor-pump unit (2) related to the rotational speed.

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