Pump unit for a transmission, in particular in a motor vehicle drive train

Abstract

The invention relates to a pump unit (10) having a double pump (16) with a suction port (26) for sucking from an external fluid reservoir (3) and having a high-pressure outlet (24) and a low-pressure outlet (22), the high-pressure outlet and the low-pressure outlet respectively leading to a first control port (K0) and at least one lubricant / coolant port (S1, S2) of the pump unit (10), and having a high-pressure pump (38) sucking from an internal fluid reservoir (14), the high-pressure pump having two high-pressure outlets (42) leading to a second and a third control port (K1, K2) of the pump unit (10), wherein a control valve (32) is arranged between the high-pressure outlet (24) and the first control port (K0) of the double pump (16), the control valve (32) having a return line (36) leading to the internal fluid reservoir (14). The invention also relates to a drive assembly having a transmission (4), having a disconnect clutch, via which the electric motor can be coupled to and disconnected from the transmission (4), and having a pump unit (10) of the above-mentioned type, wherein the suction port (26) of the pump unit (10) is connected to the oil collecting volume (3) of the transmission (4), and one of the lubricant / coolant ports (S0, S1) is used for cooling the rotor (86) and the stator (84).

Description

Technical Field

[0001] The invention relates to a pump unit which can be used to actuate clutches in a motor vehicle drive train. In particular, the drive train can be a drive train for a hybrid vehicle, that is to say a vehicle using a combustion motor and an electric motor. By means of the pump unit, the hydraulic flow required for actuating the various clutches can be provided, and the lubricant and / or coolant flow required for lubricating and / or cooling the various components can be provided. Summary of the invention

[0002] The object of the invention is to create a particularly compact pump unit which combines a plurality of different functions.

[0003] According to the invention, in order to achieve this object, a pump unit is provided, the pump unit having a double pump, the double pump having a suction port for sucking from an external fluid reservoir and having a high-pressure outlet and a low-pressure outlet, the high-pressure outlet and the low-pressure outlet leading to a first control port and at least one lubricant / coolant port of the pump unit, respectively, and having a high-pressure pump sucked from an internal fluid reservoir, the high-pressure pump having two high-pressure outlets leading to a second and a third control port of the pump unit, wherein a control valve is arranged between the high-pressure outlet and the first control port of the double pump, the control valve having a return line leading to the internal fluid reservoir. The advantage of the pump unit is that it combines two different pumps, thereby simplifying the entire installation process, because only a single component needs to be installed. The pumps are different pumps, so that different types of fluid flows can be provided. The double pump delivers a low-pressure flow and a high-pressure flow, wherein the delivery volume of the low-pressure flow is greater than the delivery volume of the high-pressure flow. The low-pressure flow can be used to lubricate the bearing points of the transmission or to cool the clutch or the electric motor. The high-pressure flow can be used to actuate the clutch. This also applies to the two high-pressure flows provided from the high-pressure outlet of the high-pressure pump. The return line of the control valve integrated into the pump unit allows the delivery flow not required at the high pressure port to be directed directly into the internal fluid reservoir, so that the internal fluid reservoir is always fully filled and the pump unit as a whole only requires one suction port to the outside.

[0004] According to a refinement of the invention, it is provided that the suction port of the pump unit and / or the high-pressure outlet of the double pump is assigned a filter. This ensures that the high-pressure pump only sucks in pre-filtered hydraulic fluid.

[0005] The double pump may be a rotary vane pump having a plurality of rotary blades which together with the stator and the rotor define a plurality of low-pressure chambers, wherein each rotary vane defines a high-pressure chamber in the rotor. With a rotary vane pump configured in this way, two different hydraulic oil flows can be provided, specifically, firstly a "normal" low-pressure flow, which is provided by the delivery chambers of different volumes formed between adjacent rotary blades. Secondly, a high-pressure flow can also be generated by the rotary vanes acting as pistons of a piston pump, the pump chamber of the piston pump being defined by the walls of the receiving grooves of the rotary vanes in the rotor, the face walls of the rotary vane pump and the face sides of the rotary vanes.

[0006] According to a refinement of the invention, a disconnect valve is provided, which is arranged between the high-pressure outlet of the double pump and the control valve of the first control port of the pump unit and whose return line leads to the internal fluid reservoir. In this way, losses are avoided, because if the pressure can be maintained by the proportional valve in the case where the clutch can be actuated without leakage, the double pump cannot simply be turned off; with regard to lubrication and cooling requirements, the double pump usually has to run continuously.

[0007] In one embodiment of the present invention, a shut-off valve is provided, which is arranged between the low-pressure outlet of the dual pump and one of the lubricant / coolant ports of the pump unit. By means of the shut-off valve, the lubricant / coolant oil flow to the clutch can be cut off when the clutch does not need cooling. In this way, the drag loss in the corresponding clutch is reduced.

[0008] In order to ensure that a minimum flow of lubrication / cooling oil is maintained, a bypass line for the shut-off valve can be provided, wherein a hole is arranged in the bypass line. With this configuration, a defined oil flow is provided, which is particularly advantageous in the case of a clutch having a hydraulic compensation chamber which should be kept filled to a defined level.

[0009] In one embodiment of the invention, an accumulation valve is arranged between the low-pressure outlet of the dual pump and one of the lubricant / coolant ports, the outlet of which is connected to the return line of the control valve, which is arranged between one of the high-pressure ports of the high-pressure pump and the second and third control ports, respectively. With the help of the accumulation valve, the low-pressure oil flow can be conducted "backwards" through the control valve to the control port and the actuator for switching the clutch. This allows the actuator to be pre-charged very quickly to the point where the high-pressure pump takes over the further supply of pressure in the event of a switching demand. This reduces the switching time.

[0010] The invention also provides a drive assembly having a transmission, having a disconnect clutch, by means of which the electric motor can be coupled to and disconnected from the transmission, and having a pump unit of the above-mentioned type, wherein the suction port of the pump unit is connected to the oil collecting volume of the transmission and one of the lubricant / coolant ports is used for cooling the rotor and the stator. A particular advantage of such a drive assembly is that only a single pump unit has to be installed, which sucks hydraulic oil from the oil collecting volume of the transmission and provides various hydraulic oil flows for switching the various clutches and an oil flow with a relatively low pressure but a relatively high volume flow, which can be used for cooling the clutches, bearing points and the electric motor.

[0011] According to a development of the invention, provision is made for a heat exchanger to be associated with one of the lubricant / coolant ports. The heat exchanger can be used to reduce the temperature of the cooling oil flow conducted to the electric motor, which has a particularly large influence on the efficiency of the electric motor.

[0012] In one embodiment, the low pressure outlet of the double pump supplies at least two lubricant / coolant ports, wherein at least one of the lubricant / coolant circuits supplied thereby is assigned a restriction or an orifice. By means of the restriction or orifice, the ratio of the volume flow through which lubricant / coolant circuit can be defined. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] The present invention will be described below based on various embodiments shown in the accompanying drawings. In these drawings:

[0014] - Figure 1 Schematically shows an assembly according to the invention having a pump unit according to the invention according to a first embodiment;

[0015] - Figure 2 An example of a double pump used in the first embodiment is schematically shown;

[0016] - Figure 3 Schematically shows a drive assembly and a pump unit according to a second embodiment of the present invention;

[0017] - Figure 4 Schematically shows a drive assembly and a pump unit according to a third embodiment of the present invention;

[0018] - Figure 5 Schematically shows a drive assembly and a pump unit according to a fourth embodiment of the present invention;

[0019] - Figure 6 Schematically shows a drive assembly and a pump unit according to a fifth embodiment of the present invention;

[0020] - Figure 7 Schematically shows a drive assembly and a pump unit according to a sixth embodiment of the present invention;

[0021] - Figure 8 Schematically shows a drive assembly and a pump unit according to a seventh embodiment of the present invention;

[0022] - Fig. 9 Schematically shows a drive assembly and a pump unit according to an eighth embodiment of the present invention;

[0023] - Fig.10 schematically illustrates a drive assembly and a pump unit according to a ninth embodiment of the present invention; and

[0024] - Fig.11 A side view of a pump unit according to the invention is shown, which pump unit can be connected to further structural elements. DETAILED DESCRIPTION

[0025] Figure 1 A first embodiment of a transmission 1 and a pump unit 10 mounted thereon is shown.

[0026] Here, in the transmission 1, a part of a transmission housing 2 is shown, in which an oil collecting volume 3 is arranged, which is an external fluid reservoir. Also schematically shown are a plurality of transmission gears 4, with which different transmission ratio steps can engage.

[0027] The pump unit 10 has a housing 12 , in the interior of which a fluid reservoir 14 is delimited.

[0028] A double pump 16 is arranged in the pump unit 10 , which is driven by an electric motor 18 .

[0029] A "double pump" is to be understood here as a hydraulic pump having a low-pressure outlet and a high-pressure outlet. The low-pressure outlet is here denoted by reference numeral 22 and the high-pressure outlet is denoted by reference numeral 24. During operation of the double pump 16, this delivers a hydraulic fluid flow with a high volume flow but a low pressure at the low-pressure outlet 22, and a hydraulic fluid flow with a low volume flow but a high pressure at the high-pressure outlet 24.

[0030] The following will refer to Figure 2 One possible configuration of the dual pump 16 is discussed further.

[0031] The dual pump 16 draws hydraulic fluid from the oil collecting volume 3 of the transmission housing 2 via a suction port 26 of the pump unit 10. Here, an oil filter 28 is provided to ensure that no contaminants enter the pump unit 10.

[0032] Generally speaking, the low-pressure port 22 of the dual pump 16 is used to supply hydraulic fluid to one or more lubricant / coolant ports of the pump unit 10. In the exemplary embodiment shown, two lubricant / coolant ports S1, S2 are provided, wherein port S1 is used to cool one or more clutches and port S2 is used to supply lubricant to the bearing points of the transmission 1.

[0033] The ports or lines through which the lubrication / cooling fluid is provided may be assigned a restrictor 30 in order to divide the volume flow in a desired manner.

[0034] The high-pressure port 24 of the dual pump 16 supplies hydraulic fluid to the first high-pressure outlet K0 of the pump unit 10. Via the high-pressure outlet K0, for example, a disconnect clutch can be switched, by which the drive motor can be coupled and disconnected.

[0035] For actuating the clutch, a control valve 32 is provided between the high-pressure outlet 24 and the high-pressure port K0 , which control valve is in this case preferably designed as an electrically actuated proportional valve to which a pressure sensor 34 is assigned.

[0036] When the control valve 32 is closed, the high-pressure fluid flow provided at the high-pressure outlet 24 of the dual pump 16 is conducted to the clutch via the high-pressure outlet K0, or more specifically, to the actuator, through which the clutch is closed. If the control valve 32 is open, part or all of the hydraulic oil flow is conducted to the fluid reservoir 14 of the pump unit 10 via the return line 36 of the control valve 32.

[0037] In the pump unit 10 , a high-pressure pump 38 is also arranged, which is driven by an electric motor 40 and which sucks in hydraulic fluid from the internal fluid reservoir 14 of the pump unit 10 via a suction channel 41 .

[0038] The high-pressure pump 38 has two high-pressure outlets 42, which are used to supply hydraulic fluid to two other high-pressure outlets K1, K2 of the pump unit 10. The two clutches actuated via the high-pressure outlets K1, K2 can be, for example, two clutches of a dual clutch, which can be actuated by the pump unit 10 so that a switch from a first transmission stage to a second transmission stage of a dual clutch transmission can be made without interrupting the traction power.

[0039] In order to be able to appropriately actuate the clutches assigned to the high-pressure ports K1 , K2 , the pump unit 10 has a second and a third control valve 44 which, like the control valve 32 , are designed as solenoid-type proportional valves and are each assigned a pressure sensor 46 .

[0040] Each control valve 44 has a return line 48 which, like the return line 36 of the control valve 32 , leads to the internal fluid reservoir 14 .

[0041] Further filters 50 may be arranged at different points within the pump unit 10. It is thereby ensured that only pre-filtered hydraulic oil is supplied to the internal fluid reservoir 14.

[0042] All hydraulic oil requirements in the transmission can be met by the pump unit 10. The dual clutch can be actuated via the high-pressure ports K1, K2 and the separating clutch can be actuated via the high-pressure port K0. In addition, each clutch can be supplied with a suitable cooling oil flow adapted to the respective requirements. For example, the thermal load of the dual clutch is 5 to 10 times higher than that of the separating clutch. Here, the high-pressure pump 38 always draws from the internal fluid reservoir 14.

[0043] Figure 2 An exemplary embodiment of a double pump 16 is shown. Here, this is a rotary vane pump having a stator 54 in which an inner space 56 is formed which is surrounded by an inner wall 58 .

[0044] The rotor 60 is arranged inside the stator 54 and is mounted on a shaft 62 and can be driven by the latter.

[0045] The rotor 60 is provided with a plurality of receptacles 64 , each of which accommodates a rotating blade 66 .

[0046] The receptacle 64 generally extends in the axial direction from one face side of the rotor 60 to the opposite face side, and extends inwardly from the outer periphery of the rotor. In the exemplary embodiment shown, the receptacle 64 extends in the radial direction. However, this is not required.

[0047] Here, the rotating blades are in the form of plates whose dimension in the radial direction is slightly smaller than the radial depth of the receptacle 64. Each plate has a thickness b which corresponds to the width of the receptacle 64.

[0048] As an alternative to plate-shaped rotor blades, it is also possible to use rotor blades in the form of cylinders.

[0049] The rotor 60 has a diameter of 2×r (minus the clearance between the rotor and the stator provided in the design), which is smaller than the diameter r+R of the inner space 56 of the stator 54. The rotor 60 is arranged eccentrically in the inner space, specifically so that it is (almost) in contact with the inner wall 8 on one side (in this case at the 6 o'clock position). Therefore, the maximum spacing to the outer wall of the rotor 60 is on the diametrically opposite side.

[0050] The rotating blades 66 are permanently in contact with the inner wall 58 of the stator 54 with their radial outer sides 68 (when the rotor 60 rotates at any rate). Thus, a low-pressure chamber 70 is defined between the rotating blades 66 adjacent to each other in the circumferential direction, the inner wall 58 of the stator 54, the outer wall of the rotor 60 and the two side walls (only the "rear" side wall 59 thereof can be seen here) that close the inner space 56 on the face side of the rotor 60.

[0051] In the exemplary embodiment shown, five low pressure chambers 70 are formed because there are five rotating blades 66. For one rotation of the rotor 60 through 360°, the volume of each individual low pressure chamber varies from a minimum value (when the low pressure chamber 70 is at approximately the 6 o'clock position) through a maximum value (when the low pressure chamber 70 is at approximately the 12 o'clock position) and back to a minimum value.

[0052] Hydraulic fluid is supplied to the low-pressure chamber 70 via an inlet 72. Said inlet is located behind the point where the spacing between the outer surface of the rotor 60 and the inner wall 58 of the stator 54 is smallest, as seen in the direction of rotation of the rotor 60.

[0053] The hydraulic fluid sucked into the low-pressure chamber 70 via the inlet 72 is delivered via the low-pressure outlet 74, which is located after the position where the low-pressure chamber 70 has the maximum volume but before the position where the distance between the outer side of the rotor 60 and the inner wall 58 of the stator 54 is the smallest, as viewed in the circumferential direction.

[0054] The inlet 72 and the low-pressure outlet 74 are arranged here in one of the side walls 59 of the hydraulic pump 16 or, for improved filling, in both side walls 59 so that hydraulic fluid can be sucked into the low-pressure chamber 70 and pushed out of the low-pressure chamber 70 from both sides.

[0055] Each rotating blade 66, together with the rotor 60 (and the side wall 59), defines a high pressure chamber 76. Specifically, each radial inner side 78 of each rotating blade 66, together with the wall and the side wall 59 of the receptacle 64 shown, defines a high pressure chamber 76.

[0056] The volume of the high-pressure chamber 76 changes according to the displacement of the rotating blade 66 in the receptacle 64. When the rotating blade 66 moves outward (that is, in the exemplary embodiment shown, during the process of moving from the 6 o'clock position via the 3 o'clock position to the 12 o'clock position), the volume of the high-pressure chamber 76 increases, and when the rotating blade 66 moves inward (that is, during the process of moving from the 12 o'clock position via the 9 o'clock position to the 6 o'clock position), the volume decreases.

[0057] In this way, a piston pump is formed, in which the radial inner side 78 of each rotating blade 66 can be regarded as the face surface of a pump piston, which is adjusted by the curved path (of the inner wall 58 of the stator 54). For suction, the pump piston is adjusted outwards under the effect of centrifugal force, and for expulsion, the pump piston is moved inwards due to the contour of the inner wall 58 of the stator 54.

[0058] The high pressure chamber 76 is drawn in via the same inlet 72 that provides supply to the low pressure chamber 70 .

[0059] A high pressure outlet 80 separated from the low pressure outlet 74 is provided on the pressure side of the high pressure pump. The high pressure outlet is arranged at substantially the same position as the low pressure outlet 74 in the circumferential direction.

[0060] The high-pressure outlet 80 can be arranged on only one of the side walls 59 of the stator 54 (and therefore also on a side wall of the rotor 60 ), or on both sides.

[0061] Figure 3 The same reference numerals are used for the components known from the first embodiment and in this respect reference is made to the above explanations.

[0062] The difference between the first and second embodiments is that, in the second embodiment, the disconnect valve 82 is arranged between the high-pressure outlet port 24 of the dual pump 16 and the first control valve 32. The disconnect valve 82 is used to discharge the hydraulic fluid delivered by the dual pump 16 at the high-pressure port 24 directly into the internal fluid reservoir 14 in an open state without the hydraulic fluid having to flow through the control valve 32. In this way, the energy required to drive the dual pump 16 can be reduced in the stage where the fluid pressure at the first high-pressure port K0 can be maintained only by the proportional valve.

[0063] Figure 4 The same reference numerals are used for components known from the preceding embodiments and in this respect reference is made to the above explanations.

[0064] The difference between the first and third embodiments is that in the third embodiment, the lubricant flow provided at the lubricant / coolant port S2 is used to cool the stator 84 and the rotor 86 of the electric motor, which are represented here only by the stator 84 and the rotor 86. The hydraulic oil then flows to the bearing points and the tooth meshing points of the gearbox gear 4.

[0065] Figure 5 A fourth embodiment is shown. The same reference numerals are used for components known from the preceding embodiments, and reference is made to the above explanations.

[0066] The difference between the third and fourth embodiments is that in the fourth embodiment a limiter 90 is provided by which the volume flow through the stator 84 and the rotor 86 can be appropriately set. In particular, a relatively large proportion of the volume flow is conducted through the stator, since more heat is generated there.

[0067] Figure 6 A fifth embodiment is shown. The same reference numerals are used for components known from the preceding embodiments and in this respect reference is made to the above explanations.

[0068] The difference between the fifth and fourth embodiments is that in the fifth embodiment, a heat exchanger 92 is provided between the lubricant / coolant port S2 and the electric motor 88, by which the temperature of the hydraulic oil used to cool the electric motor 88 is reduced. This has a particularly favorable effect on the efficiency of the electric motor 88.

[0069] Figure 7 A sixth embodiment is shown. The same reference numerals are used for components known from the preceding embodiments and in this respect reference is made to the above explanations.

[0070] The difference between the sixth embodiment and the fifth embodiment is that in the sixth embodiment, a shutoff valve 94 is provided, which is arranged between the low-pressure outlet 22 of the dual pump 16 and the first lubricant / coolant port S1 .

[0071] By means of the shut-off valve 94, the disconnecting clutch, to which the cooling medium is supplied via the lubricant / coolant port S1, can be cooled as required. After actuation, the shut-off valve 94 is opened for a period of typically 15-30 seconds, so that the desired cooling effect is achieved. The shut-off valve 94 is then closed again. In this way, drag losses in the disconnecting clutch open state can be prevented.

[0072] Figure 8 A seventh embodiment is shown. The same reference numerals are used for components known from the preceding embodiments and in this respect reference is made to the above explanations.

[0073] The difference between the sixth and seventh embodiment is that in the seventh embodiment a bypass line 96 for the shutoff valve 94 is provided. A bore 98 can be arranged in said bypass line. By means of the bypass line 96 it is ensured that a minimum volume flow via the lubricant / coolant port S1 is available even in the closed state of the shutoff valve 94. This is advantageous if a wet clutch with an internal rotary piston is involved; these require constant lubrication. Furthermore, in this way the hydraulic compensation chamber required in this clutch type for compensating the centrifugal forces of the rotating oil can remain filled.

[0074] The particular advantage of the limiter 98 is that its effect is virtually independent of the viscosity. Thus, the required volume flow can be ensured independently of the temperature of the hydraulic oil.

[0075] Fig. 9 An eighth embodiment is shown. The same reference numerals are used for components known from the preceding embodiments and in this respect reference is made to the above explanations.

[0076] The difference between the eighth and seventh embodiments is that in the eighth embodiment, the cooling oil flow provided via port S1 is divided into two separate cooling oil flows for the disconnect clutch (port K0) and the two dual clutches (ports K1, K2). Here, the volume flow can be appropriately set by a restrictor.

[0077] Fig.10 A ninth embodiment is shown. The same reference numerals are used for components known from the preceding embodiments and in this respect reference is made to the above explanations.

[0078] The difference between the ninth embodiment and the eighth embodiment is that in the ninth embodiment, an accumulation valve 100 is provided between the low-pressure outlet 22 of the dual pump 16 and the second lubricant / coolant port S2 .

[0079] If the accumulation valve 100 is open, supply is provided to port S2, similarly to the case in the previous embodiments.

[0080] If the accumulation valve 100 is closed, the volume flow of the low-pressure outlet 22 of the dual pump 16 is conducted to the return line 48 of the control valve 44 via the accumulation line 102. This enables the flow to pass through the control valve 44 "backwards", and thus the clutch actuators connected to the high-pressure ports K1, K2 can be prefilled in a very short time. In this way, in the presence of a shift demand, the corresponding clutch can be brought into the vicinity of the "bite point" very quickly. The control valve 44 then takes over the actuation of the clutch in order to control the transfer of torque from one clutch to another. For this purpose, a high-pressure fluid provided via the high-pressure outlet 42 of the high-pressure pump 38 is then required.

[0081] Fig.11 A pump unit 10 is schematically shown, which can be attached to a transmission housing (not shown in greater detail here) as a complete unit. The control valves 32, 44, 100 protrude outwards from the pump unit 10 so that they can be directly cooled by the oil in the transmission. On the rear side of the pump unit 10 a connector plug 104 can be seen, via which the pump unit 10 can be connected to a motor and / or a transmission controller. The pump unit 10 can also perform further actuation of other components, such as a module 106 for transmission actuation (schematically shown here).

Claims

1. A pump unit (10) having a double pump (16) having a suction port (26) for suction from an external fluid reservoir and having a high-pressure outlet (24) and a low-pressure outlet (22), the high-pressure outlet and the low-pressure outlet leading to a first control port (K0) and at least one lubricant / coolant port (S1, S2) of the pump unit (10), respectively, and having a high-pressure pump (38) sucking from an internal fluid reservoir (14), the high-pressure pump having two high-pressure outlets (42) leading to a second and a third control port (K1, K2) of the pump unit (10), wherein: A control valve (32) is arranged between the high-pressure outlet (24) of the dual pump (16) and the first control port (K0), and the control valve (32) has a return line (36) leading to the internal fluid reservoir (14).

2. The pump unit (10) according to claim 1, characterized in that The suction port (26) of the pump unit (10) and / or the high-pressure outlet (24) of the dual pump (16) are assigned a filter (50).

3. The pump unit according to claim 1 or 2, characterized in that The dual pump (16) is a rotary vane pump having a plurality of rotating blades (66) which, together with a stator (54) and a rotor (60), define a plurality of low pressure chambers (70), wherein each rotating blade (66) defines a high pressure chamber (76) within the rotor.

4. Pump unit according to any one of the preceding claims, characterized in that A disconnect valve (82) is provided, which is arranged between the high-pressure outlet (24) of the dual pump (16) and the control valve (32) of the first control port (K0) of the pump unit (10) and whose return line leads to the internal fluid reservoir (14).

5. Pump unit according to any one of the preceding claims, characterized in that A shutoff valve (94) is provided, which is arranged between the low-pressure outlet (22) of the dual pump (16) and the first lubricant / coolant port of the lubricant / coolant ports of the pump unit (10).

6. The pump unit according to claim 5, characterized in that A bypass line (96) is provided for the shutoff valve (94), wherein a bore (98) is arranged in the bypass line.

7. Pump unit according to any one of the preceding claims, characterized in that An accumulation valve (100) is arranged between the low-pressure outlet (22) of the dual pump (16) and the second lubricant / coolant port of the lubricant / coolant ports, and its outlet is connected to a return line (48) of a control valve (44) which is arranged between one of the high-pressure outlets (42) of the high-pressure pump (38) and the second and third control ports (K1, K2), respectively.

8. A drive assembly having a transmission (4), having a disconnect clutch, by means of which the electric motor can be coupled to and decoupled from the transmission (4), and having a pump unit (10) according to any of the preceding claims, wherein the suction port (26) of the pump unit (10) is connected to an oil collecting volume (3) of the transmission (4), and a second lubricant / coolant port of the lubricant / coolant ports is used for cooling the rotor (86) and the stator (84).

9. The drive assembly according to claim 8, characterized in that: A heat exchanger (92) is assigned to a second one of the lubricant / coolant ports.

10. The drive assembly according to any one of claims 8 and 9, characterized in that The low pressure outlet (22) of the dual pump (16) supplies at least two lubricant / coolant ports, and at least one of the lubricant / coolant circuits supplied thereby is assigned a restrictor (30) or an orifice.

Images