Valve and cooling system for a hybrid or electric motor vehicle having such a valve

Abstract

The invention relates to a valve (1) for the temperature-dependent control of two cooling circuits, namely a first cooling circuit (2) through which a first coolant flows and a second cooling circuit (3) through which a second coolant flows, characterised in that the valve (1) is designed in such a way that the coolant flow of second coolant is controlled on the basis of a state variable of the first coolant. The invention also relates to a cooling system comprising such a valve (1).

Description

[0001] Valve and cooling system for a hybrid or electric vehicle with such a valve

[0002] Field of invention

[0003] The present invention relates to a valve for controlling two cooling circuits, namely a first cooling circuit through which a first coolant flows and a second cooling circuit through which a second coolant flows, of a cooling system of a motor vehicle and a cooling system for a hybrid or electric motor vehicle comprising such a valve.

[0004] State of the art

[0005] Modern motor vehicles increasingly use electric motors as drive units to create alternatives to internal combustion engines that require fossil fuels.

[0006] In addition to purely electric powertrains, hybrid powertrains are also known. Such powertrains typically comprise a combination of an internal combustion engine and at least one electric motor, enabling both purely electric and combustion engine-driven operation. Furthermore, it is possible to simultaneously use the internal combustion engine and the motor-driven electric motor in certain operating situations.

[0007] In both purely electric and hybrid powertrains, numerous electrical and / or mechanical components of the vehicle require temperature control, in particular cooling, to dissipate the waste heat generated during their operation. This dissipation is achieved through suitable cooling systems.

[0008] Power electronics components, such as inverters, require hydraulic cooling. For example, water-cooled inverters, which are directly connected to the vehicle's overall cooling circuit, can be used to cool such an inverter.

[0009] Electrical machines typically consist of a rotor and a stator, which, during operation, are subjected to thermal stress due to the current flow through the current-carrying conductors and due to eddy current losses, hysteresis losses, and other losses. Therefore, cooling of the electrical machine becomes necessary. An oil is generally used as a coolant for cooling the electrical machine; this oil is circulated through the machine to absorb heat.

[0010] Summary of the invention

[0011] It is an object of the invention to provide a valve that can be easily integrated into a cooling system of a hybrid or electric vehicle and through which an improvement in the operating efficiency of a hybrid or electric vehicle can be achieved.

[0012] Furthermore, it is an object of the present invention to provide an improved cooling system for a hybrid or electric motor vehicle.

[0013] This need can be met by the subject matter of the present invention according to independent claims 1 and 14. Advantageous embodiments of the present invention are described in the dependent claims.

[0014] The valve according to the invention serves to control two cooling circuits of a cooling system of a hybrid or electric motor vehicle, namely a first cooling circuit through which a first coolant flows and a second cooling circuit through which a second coolant flows.

[0015] According to the present invention, the valve is designed such that the coolant flow at the second coolant is controlled depending on a state variable of the first coolant.

[0016] In this context, the term "state variable" refers to an intensive state variable, such as the temperature or pressure of the first coolant.

[0017] In a preferred embodiment of the present invention, the valve has an adjustable actuator unit comprising at least two expansion elements, namely a first expansion element with a first threshold state variable and a second expansion element with a second threshold state variable, wherein the two expansion elements are each functionally connected to the coolant flow at first coolant.

[0018] The two expansion elements can be arranged in a common chamber or each in its own chamber.

[0019] If the two expansion elements are arranged in the common chamber, they are preferably separated from each other by a floating sealing element. The actuator unit preferably has at least one adjustable component, wherein an adjustable component is connected to at least one expansion element in an adjustment-effective manner.

[0020] Particularly preferably, the actuator unit has at least two adjustable components, each of which is connected to at least one expansion element in an adjustment-effective manner, wherein one adjustable component releases or interrupts the coolant flow of the second coolant and the at least one other adjustable component releases or interrupts the coolant flow of the first coolant.

[0021] Furthermore, the actuator unit preferably has three adjustable components, each of which is connected to at least one expansion element in an adjustment-effective manner, wherein one adjustable component releases or interrupts the coolant flow at second coolant and the two other adjustable components release or interrupt the coolant flow at first coolant.

[0022] The valve is preferably designed as a multi-way valve with three switching positions, namely a first switching position, a second switching position and a third switching position.

[0023] In a particularly preferred embodiment of the valve according to the invention, the state variable of the first coolant is a temperature of the first coolant.

[0024] Taking this into account, the valve preferably has a temperature-dependent adjustable actuator unit comprising at least two expansion elements, namely a first expansion element with a first threshold temperature and a second expansion element with a second threshold temperature, wherein the two expansion elements are each thermally connected to the coolant flow of the first coolant.

[0025] In an advantageous embodiment, the valve assumes the first switching position when the temperature of the first coolant is less than or equal to the first threshold temperature, the second switching position when the temperature of the first coolant is between the first threshold temperature and the second threshold temperature, and the third switching position when the temperature of the first coolant is greater than or equal to the second threshold temperature.

[0026] The first coolant is preferably oil and the second coolant is preferably a water / glycol mixture. However, it should be noted that any coolant suitable for the respective application, liquid or gaseous, can be used.

[0027] The cooling system according to the invention is used in a hybrid or electric motor vehicle and comprises a first cooling circuit through which a first coolant flows for temperature control of at least one electric machine and / or at least one mechanical component, a second cooling circuit through which a second coolant flows for temperature control of at least one electrical and / or mechanical component and a valve according to the invention, wherein the valve is fluidly connected to the first coolant circuit and the second coolant circuit.

[0028] In addition to common temperature-sensitive wax elements, other temperature-sensitive or differently sensitive expansion elements can also be used. Brief description of the drawings.

[0029] The invention is described below by way of example with reference to the drawings.

[0030] Fig. 1 shows a schematic representation of a cooling system for a hybrid or electric motor vehicle.

[0031] Fig. 2 shows a schematic representation of a first embodiment of a valve in a first switching position.

[0032] Fig. 3 shows a schematic representation of a first embodiment of a valve in a second switching position.

[0033] Fig. 4 shows a schematic representation of a first embodiment of a valve in a third switching position.

[0034] Fig. 5 shows a schematic representation of a second embodiment of a valve in a first switching position.

[0035] Fig. 6 shows a schematic representation of a second embodiment of a valve in a second switching position.

[0036] Fig. 7 shows a schematic representation of a second embodiment of a valve in a third switching position.

[0037] Fig. 8 shows a schematic representation of a third embodiment of a valve in a first switching position. Fig. 9 shows a schematic representation of a third embodiment of a valve in a second switching position.

[0038] Fig. 10 shows a schematic representation of a third embodiment of a valve in a third switching position.

[0039] Fig. 11 shows another isometric view of a third

[0040] Design variant of a valve with a heat exchanger.

[0041] Detailed description of the invention

[0042] Figure 1 schematically shows an exemplary cooling system 9 for a hybrid or electric vehicle, into which a valve 1 according to the invention is integrated. Figures 2 to 10 show different embodiments of the valve 1 in different switching positions C, W, H.

[0043] Flow directions of a coolant within the cooling system 9 or within the valve 1 are, if applicable, schematically represented in the figures by arrows X.

[0044] The cooling system 9 according to Fig. 1 serves to regulate the temperature, in particular to cool, electrical, electronic, and mechanical components of the hybrid or electric vehicle. Fig. 1 schematically depicts components of the hybrid or electric vehicle to be regulated, such as an inverter 12, a cooling jacket 13 of a stator 14 of an electric machine, the stator 14 and the rotor 15 of the electric machine, as well as other vehicle components 16. The cooling system 9 comprises a first cooling circuit 2, a second cooling circuit 3, a coolant sump 10, a heat exchanger 11, and a valve 1. The first cooling circuit serves to cool the active components of the electric machine, namely the stator 14 and the rotor 15. The second cooling circuit serves to cool the inverter 12, the cooling jacket 13 of the stator 14, and other vehicle components 16.

[0045] The first cooling circuit 2 and the second cooling circuit 3 are two parallel cooling circuits.

[0046] The first cooling circuit 2 carries a first coolant, namely oil. The oil is located in the coolant sump 10 and is pumped from there into the first cooling circuit 2 via a filter (not shown) and a pump (not shown).

[0047] The second cooling circuit 3 uses a second coolant, namely a water / glycol mixture.

[0048] The two cooling circuits 2, 3 are thermally connected via the heat exchanger 11.

[0049] The valve 1 is functionally arranged upstream of the heat exchanger 11 with respect to a flow direction X of the oil or the water / glycol mixture.

[0050] In all illustrated embodiments, the valve 1 serves to control the first cooling circuit 2 and the second cooling circuit 3 in a temperature-dependent manner, wherein the valve 1 is designed such that the coolant flow of water / glycol mixture is controlled as a function of a temperature as a state variable of the oil.

[0051] Valve 1 is designed as a multi-way valve with three switching positions C, W, H: a first switching position C ("cold"), a second switching position W ("warm"), and a third switching position H ("hot"). Valve 1 can generally be configured as a spool valve (Figs. 8-12) or as a poppet valve (Figs. 2-7), i.e., as a seat valve.

[0052] The valve 1 has a valve housing 17 in which a temperature-dependent adjustable actuator unit 4 is arranged.

[0053] The actuator unit 4 of the valve 1 has at least two expansion elements, namely a first expansion element 5 with a first threshold temperature T1 and a second expansion element 6 with a second threshold temperature T2, as well as, depending on the embodiment, at least one adjustable component 8. An adjustable component 8 is connected to at least one expansion element 5, 6 in an adjustment-effective manner.

[0054] The two expansion elements 5, 6 are designed as wax elements in the present embodiments.

[0055] The two expansion elements 5, 6 are each thermally connected to the coolant flow of the oil.

[0056] The first threshold temperature T1 of the first expansion element 5 is lower than the second threshold temperature T2 of the second expansion element 6.

[0057] In the first embodiment according to Figs. 2 to 4, the valve 1 has a valve housing 17 in which an adjustable piston 18 is arranged. Three axially adjustable valve discs, namely a first valve disc 21, a second valve disc 22, and a third valve disc 23, are arranged on the piston 18. The piston 18 and the valve discs 21, 22, 23 arranged thereon each form an adjustable component 8 of the actuator unit 4 of the valve 1.

[0058] Each valve disc 21, 22, 23 is assigned a correspondingly designed, stationary valve seat in the valve housing 17 - the first valve disc 21 a first valve seat 24, the second valve disc 22 a second valve seat 25 and the third valve disc 23 a third valve seat 26.

[0059] The actuator unit 4 of the valve 1 of the first embodiment continues to have three coil springs, namely a first coil spring 27, a second coil spring 28 and a third coil spring 29, which, depending on the switching position, effect a corresponding (re-)position of the valve plates 21 , 22 , 23 or of the piston 18.

[0060] The first coil spring 27 is arranged between a first end section 30 of the piston 18 and the first valve plate 21. A second coil spring 28 is arranged between the first valve plate 21 and the second valve plate 22, and a third coil spring 29 is arranged between a first retaining ring 32, which is fixed to the piston 18, and the third valve plate 23. A second retaining ring 33, which is fixed to a second end section 34 of the piston 18, is arranged in a fixed position.

[0061] Valve 1 of the first embodiment has a first inlet opening 35 and a second inlet opening 36. Oil from the coolant sump 10 is supplied to valve 1 via the first inlet opening 35. The condition of the first coolant is sensed and / or measured in the area of ​​the first inlet opening 35.

[0062] The water / glycol mixture (after passing through a cooling element of the inverter 12) is supplied to the valve 1 via the second inlet opening 36.

[0063] Furthermore, the valve 1 has a third inlet opening 37. Oil coming from the heat exchanger 11 is supplied to the valve 1 via the third inlet opening 37.

[0064] The first inlet opening 35 and the third inlet opening 37 are thus assigned to the first cooling circuit 2 and the second inlet opening 36 is assigned to the second cooling circuit 3.

[0065] Furthermore, the valve 1 has several drain openings, namely a first drain opening 38, a second drain opening 39, a third drain opening 40, a fourth drain opening 41 and a fifth drain opening 42.

[0066] Oil from the first cooling circuit 2 can be supplied to the cooling of the stator 14 of the electric machine via the first drain opening 38.

[0067] The water / glycol mixture can be returned directly to the cooling of further vehicle components 16 via the second drain opening 39.

[0068] Oil from the first cooling circuit 2 can be supplied to the cooling of the rotor 15 of the electric machine via the third drain opening 40.

[0069] The water / glycol mixture can be supplied to the heat exchanger 11 via the fourth drain opening 41.

[0070] Oil can be supplied to the heat exchanger 11 via the fifth drain opening 42.

[0071] The first drain opening 38, the third drain opening 40, and the fifth drain opening 42 are thus assigned to the first cooling circuit 2, and the second drain opening 39 and the fourth drain opening 41 are assigned to the second cooling circuit 3. The two expansion elements 5 and 6 are arranged in a common chamber, separated by a floating sealing element 7, in the area of ​​the first inlet opening 35 of the valve 1 and are connected to the piston 18 and the valve discs 21, 22, 23, respectively, in a way that allows adjustment.

[0072] Figure 2 shows the first switching position C ("cold") of valve 1 in the first embodiment. In the first switching position C, the oil temperature T is lower than or equal to the first threshold temperature T1 of the first expansion element 5.

[0073] In the first switching position C, the second valve plate 22 does not seal against the second valve seat 25, and the third valve plate 23 does not seal against the third valve seat 26. In this way, the heat exchanger 11 is largely bypassed on both the oil and water / glycol sides. Due to the greater flow resistance of the heat exchanger 11 compared to the flow cross-section opened via the second valve plate 22, the oil flows primarily through the first drain opening 38 of the valve 1 directly to the cooling of the stator 14 of the electric machine. The second cooling circuit 3 is short-circuited after the inverter 12, and the water / glycol mixture, due to the greater flow resistance of the heat exchanger 11 compared to the flow cross-section opened via the third valve plate 23, flows directly back through the second drain opening 39 of the valve 1 to the cooling of other vehicle components 16.The first valve plate 21 seals against the first valve seat 24 and thus interrupts the flow of oil via the third drain opening 40 to the cooling of the rotor 15 of the electric machine.

[0074] The following advantages can be achieved by implementing the first switching position C:

[0075] - Protection of the heat exchanger 11 and prevention of high oil and water / glycol mixture pressures at seals and pump. - Reduction of the pump's energy consumption.

[0076] - Rapid heating of the electric machine due to the bypassing of the heat exchanger 11 and the cooling of the stator 14 via the cooling jacket 13. This can increase the gearbox efficiency.

[0077] - In the case of a battery storage system, no recuperation energy can be stored in the battery storage system at low battery temperatures. By operating the inverter 12 "inefficiently," the recuperation energy can be converted into heat energy and used to heat the water / glycol mixture in the second cooling circuit 3, which can, for example, contribute to faster battery heating and / or faster air conditioning of the vehicle's driver's cabin.

[0078] Figure 3 shows the second switching position W ("warm") of valve 1 in the first embodiment. In the second switching position W, the oil temperature T lies between the first threshold temperature T1 of the first expansion element 5 and the second threshold temperature T2 of the second expansion element 6.

[0079] In the second switching position W, the oil- and water / glycol mixture-side bypass of the heat exchanger 11 ("bypass to bypass the heat exchanger 11") is closed by exceeding the first threshold temperature T1 and by the expansion of the first expansion element 5. The respective flow is interrupted by pressing the second valve disc 22 with its sealing surface against the second valve seat 25 and the third valve disc 23 with its sealing surface against the third valve seat 26. This allows oil and the water / glycol mixture to flow through the heat exchanger 11, enabling heat exchange between these two media. The stator 14 is now cooled with cooled oil via the first drain opening 38.The water / glycol mixture, after passing through the heat exchanger 11, is directed via a through-opening 46 to the cooling jacket 13 of the stator 14. However, in the case of pure oil cooling of the electric machine, it can also be directed to other vehicle components 16. The first valve plate 21 remains in sealing contact with the first valve seat 24, thus interrupting the flow of oil via the third drain opening 40 to the cooling of the rotor 15 of the electric machine – the cooling of the rotor 15 of the electric machine remains deactivated.

[0080] The following advantages can be achieved by implementing the second switching position W:

[0081] - Active cooling of the stator 14.

[0082] - A reduction in rotor fling losses, since rotor cooling is not yet activated when the electric drive is at operating temperature.

[0083] Figure 4 shows the third switching position H ("hot") of valve 1 in the first embodiment. In the third switching position H, the oil temperature T is higher than or equal to the second threshold temperature T2 of the second expansion element 6.

[0084] When the temperature T of the oil exceeds the second threshold temperature T2 of the second expansion element 6, the second expansion element 6 expands and the first valve disc 21 lifts off from the first valve seat 24, releasing the flow of cooled oil to cool the rotor 15.

[0085] The following advantages can be achieved by implementing the third switching position H:

[0086] - Active cooling of the stator 14.

[0087] - Active cooling of the rotor 15 to guarantee the cooling of the rotor 15 and increase performance, especially during demanding operation of the motor vehicle, such as towing trailers, driving uphill, on racetracks, on highways, etc.

[0088] Valve 1, according to the first version variant, is also overpressure-proof and does not open at excessively high oil and / or water / glycol mixture pressures ("Normally Closed" version).

[0089] In order to actively control the temperature-controlled valve 1, the two expansion elements 5, 6 can be heated independently of each other by an electric heating element 43.

[0090] In contrast to the first embodiment of valve 1 according to Figs. 2 to 4, in the second embodiment of valve 1 according to Figs. 5 to 7, the two expansion elements 5, 6 are each arranged in a separate chamber. The construction of valve 1 in the second embodiment therefore differs from that of the first embodiment; however, only the differing parts or components will be described below. For the other components, please refer to the description of the first embodiment of valve 1. Furthermore, the operating principle of valve 1 in the second embodiment essentially corresponds to that of the first embodiment and will therefore not be described again. In this context, please also refer to the description of the first embodiment of valve 1, as illustrated in Fig.Fig. 5 shows the first switching position C of the valve 1 of the second embodiment, Fig. 6 shows the second switching position W of the valve 1 of the second embodiment and Fig. 7 shows the third switching position H of the valve 1 of the second embodiment.

[0091] In the second embodiment of the valve 1 according to Figures 5 to 7, the valve 1 has a valve housing 17 in which two axially adjustable pistons, namely a first piston 19 and a second piston 20, are arranged. A first valve disc 21 is fixed to the first piston 19, i.e., axially fixed and rotationally fixed. Two axially adjustable valve discs, namely a second valve disc 22 and a third valve disc 23, are arranged on the second piston 20. The first piston 19 is guided axially movable in an opening of the axially movable second piston 20. The two pistons 19, 20 and the valve discs 21, 22, 23 arranged thereon each form an adjustable component 8 of the actuator unit 4 of the valve 1.

[0092] Each valve disc 21, 22, 23 is assigned a correspondingly designed, stationary valve seat in the valve housing 17 - the first valve disc 21 a first valve seat 24, the second valve disc 22 a second valve seat 25 and the third valve disc 23 a third valve seat 26.

[0093] The actuator unit 4 of the valve 1 of the second version variant continues to have three coil springs which, depending on the switching position, effect a corresponding (re-)position of the valve plates 21 , 22, 23 or of the two pistons 19, 20 independently of each other.

[0094] A first coil spring 27 is arranged between the valve housing 17 and the first valve plate 21. A second coil spring 28 is arranged between a correspondingly shaped shoulder of the second piston 20 and the second valve plate 22, and a third coil spring 29 is arranged between a stationary retaining ring 31 on the second piston 20 and the third valve plate 23.

[0095] The first expansion element 5 is arranged in a first chamber and is connected, in an adjustment-effective manner, to the second piston 20 and the two valve discs 22, 23 associated with the second piston. The second expansion element 6 is arranged in a second chamber and is connected, in an adjustment-effective manner, to the first piston and the first valve disc 21. Both expansion elements 5, 6 are arranged in the region of the first inlet opening 35 of the valve 1.

[0096] The third embodiment of valve 1 according to Figures 8 to 12, like the second embodiment of valve 1, has two adjustable pistons 19, 20. The two expansion elements 5, 6 are each arranged in a separate chamber. Figure 12 shows a perspective view of the third embodiment of valve 1. The following discussion focuses primarily on the structural differences between the third embodiment of valve 1 and the second embodiment of valve 1.

[0097] In the third embodiment of the valve 1 according to Fig. 8 to Fig. 12, the valve 1 has a valve housing 17 in which two adjustable pistons, namely a first piston 19 and a second piston 20, are arranged, wherein the two pistons 19, 20 are arranged separately from each other.

[0098] Furthermore, the first piston 19 is adjustable via a first sliding sleeve 44, and the second piston 20 is adjustable via a second sliding sleeve 45. Each piston 19, 20 and its associated sliding sleeve 44, 45 each constitute an adjustable component 8 of the actuator unit 4.

[0099] The first expansion element 5 is arranged in a first chamber and is connected to the first piston 19 in an adjustment-effective manner. The second expansion element 6 is arranged in a second chamber and is connected to the second piston 20 in an adjustment-effective manner. Both expansion elements 5 and 6 are arranged in the region of the first inlet opening 35 of the valve 1.

[0100] Figure 8 shows the first switching position C ("cold") of valve 1 in the third embodiment. In the first switching position C, as in the previously described embodiments, the heat exchanger 11 is bypassed on both sides, i.e., in both the first cooling circuit 2 and the second cooling circuit 3. The first coolant, i.e., oil, is supplied to valve 1 via the first inlet opening 35. In the area of ​​the first inlet opening 35, both the first expansion element 5 and the second expansion element 6 are thermally connected to the oil.

[0101] In the first switching position C of the valve 1, a bypass to the first drain opening 38 is opened via the position of the first piston 19 and the first sliding sleeve 44, bypassing the heat exchanger 11. The first coolant flows via the first drain opening 38 to cool the stator 14. The third drain opening 40 is closed by the first sliding sleeve 44, and the cooling of the rotor 15 is therefore inactive.

[0102] The second coolant, i.e., the water / glycol mixture, is supplied to valve 1 via the second inlet opening 36. In the first switching position C of valve 1, a bypass to bypass the heat exchanger 11 is opened via the position of the second piston 20 and the second sliding sleeve 45, and the second coolant can be routed to other vehicle components via the second outlet opening 39.

[0103] Figure 9 shows the second switching position W ("warm") of valve 1 in the third embodiment. In the second switching position W, the bypass for circumventing the heat exchanger 11 is closed via the first piston 19 and the first sliding sleeve 44, and the first coolant flows via the heat exchanger 11 to the third inlet opening 37 and from there to the first outlet opening 38. From there, the cooled first coolant is directed to cool the stator 14. The third outlet opening 40 remains closed by the first sliding sleeve 44, thus keeping the cooling of the rotor 15 inactive.

[0104] In the second switching position W of the valve 1 of the third design variant, in the area of ​​the second cooling circuit 3, the bypass to circumvent the heat exchanger 11 is also closed via the second piston 20 and the second sliding sleeve 45, whereby the second coolant is directed from the second inlet opening 36 to the fourth outlet opening 41 and thus via the heat exchanger 11 and after the heat exchanger 11 via the through-opening 46 to the cooling jacket 13 of the stator.

[0105] Figure 10 shows the third switching position H ("hot") of valve 1 in the third embodiment. This differs from the second switching position W in that the first piston 19 and the first sliding sleeve 44 open the third outlet 40 for cooling the rotor 15. Thus, both the rotor 15 and the stator 14 are cooled with the first coolant. In the third switching position H of valve 1, the second piston 20 and the second sliding sleeve 45 have sufficient space to compensate for the "excess stroke," which occurs when the wax has already completely liquefied and is still expanding. The bypass for the second outlet 39, which bypasses the heat exchanger 11, remains closed by the second sliding sleeve 45, allowing the second coolant to flow from the second inlet 36 through the heat exchanger 11.

[0106] Fig. 11 shows a possible structural arrangement of the heat exchanger 11 on the valve 1 of the third embodiment variant.

[0107] List of reference signs

[0108] valve

[0109] First cooling circuit

[0110] Second cooling circuit

[0111] actuator unit

[0112] First expansion element

[0113] Second expansion element

[0114] Floating sealing element

[0115] Adjustable component

[0116] Cooling system

[0117] Coolant sump

[0118] Heat exchanger

[0119] Inverter

[0120] Cooling jacket

[0121] stator

[0122] rotor

[0123] Other automotive components

[0124] Valve housing

[0125] Pistons

[0126] First piston

[0127] Second piston

[0128] First valve plate

[0129] Second valve plate

[0130] Third valve plate

[0131] First valve seat

[0132] Second valve seat

[0133] Third valve seat

[0134] First coil spring 8 Second coil spring 9 Third coil spring 0 First end section (of the piston) 1 Retaining ring 2 First retaining ring 3 Second retaining ring 4 Second end section (of the piston)

[0135] 35 First inlet opening

[0136] 36 Second inlet opening

[0137] 37 Third inlet opening

[0138] 38 First drain opening

[0139] 39 Second drain opening

[0140] 40 Third drain opening

[0141] 41 Fourth drain opening

[0142] 42 Fifth drain opening

[0143] 43 Electric heating element

[0144] 44 First sliding sleeve

[0145] 45 Second sliding sleeve

[0146] 46 Passage opening

[0147] T Temperature of the first coolant

[0148] T1 First threshold temperature

[0149] T2 Second threshold temperature

[0150] C First switching position (“Cold”)

[0151] W Second switch position ("Warm")

[0152] Third switch position (“Hot”)

[0153] X Flow direction

Claims

Patent claims 1. Valve (1 ) for controlling two cooling circuits, namely a first cooling circuit (2) through which a first coolant flows and a second cooling circuit (3) through which a second coolant flows, characterized in that the valve (1) is designed such that the coolant flow at the second coolant is controlled as a function of a state variable of the first coolant.

2. Valve (1) according to claim 1, characterized in that the valve (1) has an adjustable actuator unit (4) comprising at least two expansion elements, namely a first expansion element (5) with a first threshold state variable and a second expansion element (6) with a second threshold state variable, wherein the two expansion elements (5, 6) are each functionally connected to the coolant flow at first coolant.

3. Valve (1) according to claim 2, characterized in that the two expansion elements (5, 6) are arranged in a common chamber or each in a separate chamber.

4. Valve (1 ) according to claim 3, characterized in that the two expansion elements (5, 6) are separated from each other in the common chamber by a floating sealing element (7).

5. Valve (1) according to one of claims 2 to 4, characterized in that the actuator unit (4) has at least one adjustable component (8, 18, 19, 20, 21, 22, 23, 44, 45), wherein an adjustable component (8, 18, 19, 20, 21, 22, 23, 44, 45) is connected to at least one expansion element (5, 6) in an adjustment-effective manner.

6. Valve (1) according to one of claims 2 to 5, characterized in that the actuator unit (4) has at least two adjustable components (8, 18, 19, 20, 21, 22, 23, 44, 45) which are each connected to at least one expansion element (5, 6) in an adjustment-effective manner, wherein one adjustable component (8, 18, 20, 23, 45) releases or interrupts the coolant flow at second coolant and the at least one other adjustable component (8, 18, 19, 20, 21, 22, 44) releases or interrupts the coolant flow at first coolant.

7. Valve (1) according to one of claims 2 to 6, characterized in that the actuator unit (4) has three adjustable components (8, 18, 19, 20, 21, 22, 23) which are each connected to at least one expansion element (5, 6) in an adjustment-effective manner, wherein one adjustable component (8, 18, 20, 23) releases or interrupts the coolant flow at second coolant and the two other adjustable components (8, 18, 19, 20, 21, 22) release or interrupt the coolant flow at first coolant.

8. Valve (1) according to one of the preceding claims, characterized in that the valve (1) is designed as a multi-way valve with three switching positions, namely a first switching position (C), a second switching position (W) and a third switching position (H).

9. Valve (1) according to one of claims 1 to 7, characterized in that the state variable of the first coolant is the temperature (T) of the first coolant.

10. Valve (1) according to claim 9, characterized in that the valve (1) has a temperature-dependent adjustable actuator unit (4) comprising at least two expansion elements, namely a first expansion element (5) with a first threshold temperature (T1) and a second expansion element (6) with a second threshold temperature (T2), wherein the two expansion elements (5, 6) are each thermally connected to the coolant flow at first coolant.

11. Valve (1) according to claim 10, characterized in that the first threshold temperature (T1) is lower than the second threshold temperature (T2).

12. Valve (1) according to claim 11, characterized in that the valve (1) assumes the first switching position (C) at a temperature (T) of the first coolant less than or equal to the first threshold temperature (T1), the second switching position (W) at a temperature (T) of the first coolant between the first threshold temperature (T1) and the second threshold temperature (T2), and the third switching position (H) at a temperature (T) of the first coolant greater than or equal to the second threshold temperature (T2).

13. Valve (1) according to one of the preceding claims, characterized in that the first coolant is oil and the second coolant is a water / glycol mixture.

14. Cooling system (9) for a hybrid or electric motor vehicle comprising a first cooling circuit (2) through which a first coolant flows for temperature control of at least one electric machine and / or at least one mechanical component, -a second cooling circuit through which a second coolant flows (3) for temperature control of at least one electrical and / or mechanical component and - a valve (1 ) according to one of claims 1 to 13, wherein the valve (1 ) is fluidly connected to the first cooling circuit (2) and the second cooling circuit (3).

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