• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Hydraulic system for a double clutch gearbox Hydraulic system (HY) for a double clutch gearbox (G) of a motor vehicle powertrain, in which the hydraulic system (HY) comprises a first pump (EP) intended for supplying pressure to a first pressure circuit (H1) and a second pump (MP) intended for supplying pressure to a second pressure circuit (H2), in which the first pressure circuit ( H1) is provided at least for the hydraulic actuation of a double clutch (K1, K2) of the double clutch gearbox (G), and the second pressure circuit (H2) is provided at least for the lubrication of other components of the double clutch gearbox (G), in which the first pump (EP) can be driven by an electric motor (EM1) assigned exclusively to the first pump (EP) which is not designed for the drive automotive vehicle, wherein the second pump (MP) can be driven by a drive unit (VM, EM2) of the powertrain of a motor vehicle. The invention further relates to a method of operating the hydraulic system (HY) and a dual-clutch gearbox (G) with the hydraulic system (HY). Figure for the abstract: Figure 2
    公开号:FR3085195A1
    申请号:FR1909396
    申请日:2019-08-26
    公开日:2020-02-28
    发明作者:Alexander Haberstock；Thilo Schmidt
    申请人:ZF Friedrichshafen AG；
    IPC主号:
    专利说明:

    Description
    Title of the invention: Hydraulic system for a double clutch transmission [0001] The invention relates to a hydraulic system for a double clutch transmission of a powertrain of a motor vehicle. The invention also relates to a double-clutch gearbox provided with such a hydraulic system and to a method of operating such a hydraulic system.
    A hydraulic control for a dual clutch gearbox is described for example in DE 10 2014 216 648 AL In one embodiment, a source of hydraulic power for this control comprises a first hydraulic pump and a second hydraulic pump . The first hydraulic pump can be driven by a heat engine and is used to supply pressure to a high-pressure circuit through which the double clutch can be actuated. The second hydraulic pump can be driven by an electric machine and is used to supply a cooling circuit. In another embodiment, the two hydraulic pumps can be driven both by the heat engine and by the electric machine.
    The command known according to the prior art offers the advantage that it is not necessary to derive all of the pressurized oil for the cooling circuit from the high pressure circuit. However, the pressure oil required for the high pressure circuit produced by the first pump driven by the heat engine must still be adjusted to the required quantity.
    The objective of the present invention is to obtain a hydraulic system for a dual-clutch gearbox which is characterized by a low energy requirement.
    This objective is achieved thanks to a hydraulic system for a dual-clutch gearbox of a motor vehicle powertrain, in which the hydraulic system comprises a first pump intended for supplying pressure to a first circuit. pressure and a second pump for supplying pressure to a second pressure circuit, in which the first pressure circuit is provided at least for the hydraulic actuation of a double clutch of the double clutch gearbox , and the second pressure circuit is provided at least for the lubrication of other components of the dual-clutch gearbox, in which the first pump is driven by an electric motor assigned exclusively to the first pump, the electric motor does not not being configured for driving the motor vehicle, the second pump being driven by a drive unit dragging of the motor vehicle powertrain.
    Advantageous developments are described in the dependent claims, the description and the figures.
    In particular, according to the dependent claims, the hydraulic system comprises one or more of the following characteristics, taken in isolation or in any technically possible combination:
    - no other consumer is assigned to the first pressure circuit except for the actuation of the double clutch;
    - The first pressure circuit is provided for the actuation of a cut-off clutch between two drive units of the powertrain of the motor vehicle, in which no other consumer is assigned to the first pressure circuit at l except the actuation of the double clutch and a hydraulic actuation of the cut-off clutch;
    - the second pressure circuit is provided for the actuation of clutch actuators of the dual-clutch gearbox;
    - An output of the first pump is connected directly to the first pressure circuit, in which a pressure in the first pressure circuit can be adjusted by regulating the speed of the electric motor assigned to the first pump;
    - An output of the first pump is connected to the first pressure circuit via a pressure limiting valve, in which the pressure limiting valve is controlled or is adjusted to a non-variable limit pressure;
    - The second pump is produced as a constant flow pump;
    - The second pump is produced as a variable flow pump;
    - An output of the second pump is connected to the second pressure circuit through a second pressure limiting valve, in which the second pressure limiting valve is controlled by means of a control valve pressure;
    - the first and second pressure circuits are connected to each other by a valve so that the first pressure circuit can be supplied with hydraulic fluid by the second pressure circuit;
    - the valve is a non-return valve; and the hydraulic system comprises an electronic control unit intended for controlling the latter.
    The invention further relates to a method of operating a hydraulic system as mentioned above in which the electronic control unit regulates the pressure in the second pressure circuit according to a volume flow requirement of the first circuit pressure.
    According to an advantageous embodiment of the above method, the electronic control unit regulates the pressure in the second pressure circuit as a function of the volume flow requirement of the first pressure circuit, so that the pressure in the second pressure circuit exceeds the pressure in the first pressure circuit so that the pressure supply to the second pressure circuit is carried out by the second pump.
    The invention further relates to a double clutch gearbox for a motor vehicle powertrain, characterized by a hydraulic system as previously described.
    A hydraulic system for a dual-clutch gearbox of a motor vehicle powertrain is proposed. The hydraulic system includes a first pump for supplying pressure to a first pressure circuit and a second pump for supplying pressure to a second pressure circuit. The first pump is used at least for the hydraulic actuation of a double clutch of the double clutch gearbox while the second pressure circuit is used at least for the lubrication of other components of the double clutch gearbox.
    According to the invention, it is expected that the first pump can be driven by its own electric motor. This electric motor is independent of a motor vehicle drive and is used exclusively for driving the first pump. The second pump can be driven by a drive unit of the powertrain of the motor vehicle, thus for example by a heat engine and / or by an electric motor arranged for driving the motor vehicle.
    Since the pressure supply for actuating the double clutch is effected by means of the first pump driven by the electric motor, the need for the volume flow rate of the first pressure circuit can be covered independently of the engine speed range. If the double clutch is not actuated, it suffices to cover the leakage oil requirement of the first pressure circuit for which only a low energy expenditure is necessary. For the lubrication pressure supply, only a small pressure is necessary in comparison with the maximum need of the first pressure circuit so that the energy consumption of the second pump is relatively low.
    Preferably, apart from actuating the double clutch, no other hydraulic consumer is assigned to the first pressure circuit. Due to the small number of consumers, the need for leakage oil from the first pressure circuit is also low.
    If the dual-clutch gearbox is part of a hybrid powertrain, a cut-off clutch is often provided between the drive units of the hybrid powertrain. Such a hybrid powertrain is described for example in DE 10 2010 003 442 A1. Preferably, a hydraulic actuation of the cut-off clutch is also assigned to the first pressure circuit, the actuation of the double clutch and the actuation of the The cut-off clutch being the only consumers of the first pressure circuit. The hydraulic requirements of the cut-off clutch actuation are very similar to the hydraulic requirements of the double-clutch actuation so that an integration of the cut-off clutch actuation into the first pressure circuit is advantageous . Since all other hydraulic consumers are supplied by the second pressure circuit, the need for leakage oil to be covered by the first pump is still low.
    As is generally known, for the representation of the reports of a double clutch gearbox, it is necessary, in addition to the double clutch, also to actuate clutches which are assigned to the partial gearboxes of the double clutch gearbox . These clutches are generally produced as claw clutches and can for example be actuated by means of control drums or control rods. The actuation can be carried out for example hydraulically or electromechanically. In the case of a hydraulic actuation of the clutches, the pressure supply of this actuation is preferably carried out through the second pressure circuit. In fact, claw clutches only need actuation energy for clutching or disengaging, but have little or no energy required to maintain the engaged or disengaged state. On the contrary, double clutches are usually produced in the form of slats with load-controlled lamellae which - for example in the case of a Normally Open clutch - must be permanently supplied with actuating energy to maintain the 'closed state. Therefore, the assignment of the clutch actuators to the second pressure circuit promotes the energy efficiency of the hydraulic system.
    According to a possible embodiment, a pressure output of the first pump is connected directly to the first pressure circuit. In other words, between the pressure outlet of the first pump and the first pressure circuit, there is no valve arranged for the reduction of pressure or the limitation of pressure. It is however possible to provide a check valve which prevents a back flow of the hydraulic fluid from the second pressure circuit towards the pressure outlet of the first pump. By regulating the speed of the electric motor which drives the first pump, the pressure in the first pressure circuit can be adjusted accordingly. Such a design of the hydraulic system is particularly energy efficient since no adjustment of the outlet pressure of the first pump is necessary. A pressure sensor can be used to detect the pressure in the first pressure circuit. Instead, for the appreciation of the pressure in the first pressure circuit, it is possible to use a pressure model which reproduces a relation between the performance of the electric motor, the temperature of the hydraulic fluid, the volume flow absorbed of hydraulic consumers and expected leaks.
    According to another possible embodiment, the output of the first pump is connected to the first pressure circuit by means of a pressure limiting valve. The pressure limiting valve can be controlled or adjusted to a non-variable limit pressure. If, in the first pressure circuit, the pressure reaches the non-variable or variable limit pressure by means of the pilot control, the output of the first pump is connected to the reservoir of the hydraulic system or to a suction connection of the first pump. Such a design of the hydraulic system reduces the charges for controlling or respectively regulating the first pump.
    Preferably, the second pump is produced as a constant flow pump, that is to say as a pump with a stable delivery volume in the presence of a constant speed. The use of such a pump is particularly inexpensive without significantly compromising the energy efficiency of the hydraulic system. In another solution, the second pump can be produced as a variable flow pump, that is to say as a pump with a variable delivery volume in a controlled manner in the presence of a constant speed. Such a solution would further improve the energy efficiency of the hydraulic system.
    Preferably, an output of the second pump is connected to the second pressure circuit by means of a second pressure limiting valve, the second pressure limiting valve being controlled by means of a control valve. pressure. Therefore, the pressure in the second pressure circuit can be increased or lowered respectively if necessary.
    Preferably, the first and second pressure circuits are connected together by a valve, particularly preferably by a non-return valve, so that the consumers of the first pressure circuit can be supplied with hydraulic fluid by the bias of the second pressure circuit. Such an embodiment makes it possible to maintain at a low level the maximum necessary volume flow of the first pump by the fact that, in situations of high need for volume flow of the first pressure circuit, the supply thereof 'performed by the second pump. Such situations are generally only short-lived and therefore only have a minor impact on the energy efficiency of the hydraulic system.
    An electronic control unit can be assigned to the hydraulic system, which receives signals from at least one sensor, is in communication link with other control units, and controls the actuators of the hydraulic system as a function of the signals. at least one sensor and based on other signals and information.
    The invention further relates to a method of operating the hydraulic system described above, according to which the control unit regulates the pressure in the second pressure circuit as a function of the volume flow requirement of the first pressure circuit. The pressure control valve can for example be used for this. The control unit can in this case increase the pressure in the second pressure circuit to the point that it exceeds the pressure in the first pressure circuit so that the consumers of the first pressure circuit are supplied with hydraulic fluid by the second pump instead of being pumped by the first pump.
    The invention also relates to a dual-clutch gearbox for a motor vehicle powertrain equipped with the hydraulic system described above. The dual-clutch gearbox may further include an electric machine which is arranged for driving the motor vehicle. The dual clutch transmission may include a cut-off clutch which is disposed in the force flow between a heat engine of the powertrain and the dual clutch of the dual clutch transmission.
    Examples of embodiments of the invention are described below in detail using the attached figures.
    [Fig.l] Figure 1 shows a schematic representation of a dual clutch gearbox; just as [0038] [fig.2] Figure 2, [0039] [fig.3] Figure 3, [0040] [fig.4] Figure 4 and [0041] [fig.5] Figure 5 each show a connection diagram of different embodiments of the hydraulic system according to the invention.
    [0042] FIG. 1 shows a schematic representation of a double-clutch gearbox G fitted with a HY hydraulic system. The motor vehicle gearbox G has a connection shaft AN which can be connected to a drive shaft GW1 by means of a cut-off clutch KO. A VM heat engine is connected to the AN connection shaft. A rotor of an EM2 electric machine is connected to the GW1 drive shaft. The dual-clutch gearbox G has a clutch section GK which houses a first clutch Kl and a second clutch K2. The two clutches Kl, K2 form a double clutch. The closure of the first clutch Kl makes it possible to connect the drive shaft GW1 to a first partial gearbox. Closing the second clutch K2 allows the GW1 drive shaft to be connected to a second partial gearbox. In a shift section GW, different stages of ratios can be formed between the partial gearboxes and an output shaft GW2 by means of a gear train not shown. The gear stages are engaged or respectively triggered for example by means of two speed control cylinders STI, ST2.
    The hydraulic system HY is supplied with pressure by means of a first pump EP and a second pump MP. The first EP pump is driven by an electric motor EM1 assigned exclusively to the first EP pump. The second pump MP is driven by the drive shaft GW1 which is driven by the electric machine EM2 or respectively, when the cut-off clutch KO is closed, by the heat engine VM. The two pumps EP, EM draw hydraulic fluid from a reservoir T of the hydraulic system HY and transport the hydraulic fluid to the consumers of the hydraulic system HY. The dual-clutch transmission G has an electronic control unit ECU which is arranged at least for controlling the hydraulic system HY.
    The structure of the double-clutch gearbox G illustrated in Figure 1 should be considered as an example only. The dual-clutch gearbox G could also be produced without the electric machine EM2 and without the cut-off clutch KO so that the thermal engine VM is permanently connected to the drive shaft GW 1.
    [0045] FIG. 2 shows a connection diagram of the hydraulic system HY according to a first embodiment of the invention. The hydraulic system HY comprises a first pressure circuit H1 and a second pressure circuit H2. The first pressure circuit H1 is provided for the actuation of the two clutches Kl, K2 of the double clutch and for the actuation of the cut-off clutch KO. A pressure control valve VK1, VK2, VK0 is assigned to each of the clutches Kl, K2, KO. By means of the pressure control valves VK1, VK2, VK0, the pressure in the first pressure circuit H1 can be adjusted to a level necessary for the actuation of the respective clutch Kl, K2, KO. If the dual-clutch gearbox G does not have a cut-off clutch KO, the pressure control valve VK0 disappears accordingly.
    The second pressure circuit H2 is separated from the first pressure circuit H1 by an RS-V valve and comprises, for example, three consumer circuits H2_KS, H2_AK and H2_DI. The H2_KS consumer circuit is used to cool and lubricate the double-clutch gearbox G. The H2_AK consumer circuit is used to actuate the STI, ST2 speed control cylinders by means of which the gearbox clutches G double clutch gears are activated. The H2_DI consumer circuit, which is optional only, is used, for example, to actuate central synchronization of the dual-clutch gearbox G if such synchronization is provided.
    The first pressure circuit H1 is directly connected to an output of the first pump EP so that the output pressure of the first pump EP directly defines the pressure in the first pressure circuit Hl. Regulating the speed of the first pump EP makes it possible to adjust the pressure in the first pressure circuit H1 accordingly. The second pressure circuit H2 is connected to the second pump MP by means of a pressure limiting valve DB-V2. If the output pressure of the second MP pump reaches or exceeds a limit value, the output of the second MP pump is connected to the suction connection of the second MP pump. This limit value is a function of a spring pre-tension of the pressure limiting valve DB-V2 and a pilot force which can be adjusted by a pressure control valve EDS_MOP.
    Figure 3 shows a connection diagram of the hydraulic system HY according to a second embodiment of the invention in which a pressure limiting valve DB-V1 is disposed between the outlet of the first EP pump and the first circuit pressure Hl. If the outlet pressure of the first EP pump reaches or exceeds a limit value, the outlet of the first EP pump is connected to a suction connection of the first EP pump. This limit value is a function of a spring preload of the pressure limiting valve DB-V1 and a pilot force which can be adjusted by a pressure control valve EDS_EOP.
    [0049] FIG. 4 shows a connection diagram of the hydraulic system HY according to a third example embodiment of the invention which essentially corresponds to the second example embodiment shown in FIG. 3. The EDS_EOP pressure control valve disappears here, so that the DBVI pressure limiting valve is set to a non-variable limit pressure.
    [0050] FIG. 5 shows a connection diagram of the hydraulic system HY according to a fourth embodiment of the invention which essentially corresponds to the third embodiment shown in FIG. 4. The second pump MP is here produced as a variable flow pump, that is to say as a pump with variable delivery volume in a controlled manner in the presence of a constant speed. Such an embodiment of the second pump MP is also possible in the other embodiments of the hydraulic system HY.
    In all the embodiments of the hydraulic system HY, the consumers of the first pressure circuit Hl have a need for high pressure and a need for low volume flow. Due to the low volume flow requirement of the first pressure circuit H1, the drive power to be applied for the first pump EP is low. The consumer circuit H2_KS of the second pressure circuit H2 needs only little pressure, but on the other hand an increased volume flow in comparison with the first pressure circuit Hl. Due to the low pressure, the drive power of the second MP pump to be applied for the H2_KS consumer circuit is low. If the other consumer circuits H2_AK, H2_DI of the second pressure circuit H2 require a higher pressure, the pressure in the second pressure circuit H2 can be increased by the control of the pressure control valve EDS_MOP for the duration of the request .
    Due to the connection of the two pressure circuits HI, H2 via the RS-V valve, the delivery volume of the first EP pump can be kept at a low level. Indeed, in case of need for an increased volume flow of the consumers of the first pressure circuit Hl, for example during a speed change process of the double clutch gearbox G, the supply of the first pressure circuit Hl can be performed when necessary by the second MP pump. For this, the pressure control valve EDS_MOP is controlled so that the pressure in the second pressure circuit H2 becomes higher than the pressure in the first pressure circuit Hl. As a result, the RS-V valve constituted as a non-return valve opens automatically. If the HY hydraulic system includes the pressure limiting valve DB-V1, the limiting pressure of the pressure limiting valve DB-V1 must either be chosen or adjusted by means of the pressure control valve EDS_EOP so that that, in this operating state, no connection is established from the second pressure circuit H2 to the suction connection of the first pump EP by means of the pressure limiting valve DB-V1. At the end of the speed change process, the pressure in the second pressure circuit H2 is lowered again by a corresponding control of the pressure control valve EDS_MOP so that the first pump EP again supplies the first pressure circuit Hl.
    Reference marks [0054] G Double clutch gearbox [0055] VM Thermal engine [0056] AN Connection shaft [0057] KO Cut-off clutch [0058] EM2 Electric machine [0059] GW 1 Drive shaft [ 0060] GW2 Output shaft [0061] GC Gearbox housing [0062] GK Clutch section [0063] Kl, K2 Double clutch [0064] GW Gear shift section [0065] STI, ST2 Control cylinder speeds [ECU] Electronic control unit [0067] HY Hydraulic system [0068] EP First pump [0069] EM 1 Electric motor [0070] MP Second pump [0071] T Tank [0072] H1 First pressure circuit [0073] H2 Second pressure circuit [0074] VK1 Pressure control valve [0075] VK2 Pressure control valve [0076] VK0 Pressure control valve [0077] RS-V Valve [0078] DB-V1 Pressure relief valve EDS-EOP Pressure control valve [0080] DB-V2 Pressure limiting valve [0081] ED S-ΜΟΡ Pressure control valve [0082] H2_KS Consumer circuit [0083] H2_AK Consumer circuit [0084] H2_DI Consumer circuit
    权利要求:
    Claims (1)
    [1" id="c-fr-0001]
    Claims [Claim 1] Hydraulic system (HY) for a double clutch gearbox (G) of a motor vehicle powertrain, in which the hydraulic system (HY) comprises a first pump (EP) intended for supplying pressure to a first pressure circuit (Hl) and a second pump (MP) for supplying pressure to a second pressure circuit (H2), in which the first pressure circuit (Hl) is provided at least for actuation hydraulic of a double clutch (Kl, K2) of the double clutch gearbox (G), and the second pressure circuit (H2) is provided at least for the lubrication of other components of the double gearbox clutch (G), characterized in that the first pump (EP) can be driven by an electric motor (EM1) assigned exclusively to the first pump (EP), the electric motor (EM1) not being configured for driving the motor vehicle, the second me pump (MP) is trainable by a drive unit (VM, EM2) of the powertrain of a motor vehicle. [Claim 2] Hydraulic system (HY) according to claim 1, characterized in that no other consumer is assigned to the first pressure circuit (Hl) except for the actuation of the double clutch. [Claim 3] Hydraulic system (HY) according to claim 1, characterized in that the first pressure circuit (Hl) is provided for actuating a cut-off clutch (KO) between two drive units (VM, EM2) of the group motor vehicle powertrain, in which no other consumer is assigned to the first pressure circuit (Hl) except for the actuation of the double clutch and a hydraulic actuation of the cut-off clutch (KO). [Claim 4] Hydraulic system (HY) according to one of the preceding claims, characterized in that the second pressure circuit (H2) is provided for the actuation of actuators (STI, ST2) of clutches of the double clutch gearbox (G). [Claim 5] Hydraulic system (HY) according to one of the preceding claims, characterized in that an outlet of the first pump (EP) is connected directly to the first pressure circuit (Hl), in which a pressure in the first pressure circuit ( Hl) can be adjusted by regulating the speed of the electric motor (EM1) assigned to the first
    pump (EP). [Claim 6] Hydraulic system (HY) according to one of claims 1 to 4, characterized in that an output of the first pump (EP) is connected to the first pressure circuit (Hl) by means of a pressure limiting valve (DB-V1), in which the pressure limiting valve (DB-V1) is controlled or is adjusted to a non-variable limit pressure. [Claim 7] Hydraulic system (HY) according to one of the preceding claims, characterized in that the second pump (MP) is produced as a constant flow pump. [Claim 8] Hydraulic system (HY) according to one of claims 1 to 6, characterized in that the second pump (MP) is produced as a variable flow pump. [Claim 9] Hydraulic system (HY) according to one of claims 1 to 8, characterized in that an output of the second pump (MP) is connected to the second pressure circuit (H2) via a second pressure limiting valve pressure (DB-V2), in which the second pressure limiting valve (DB-V2) is controlled by means of a pressure control valve (EDS_MOP). [Claim 10] Hydraulic system (HY) according to one of the preceding claims, characterized in that the first and second pressure circuits (Hl, H2) are connected to each other by a valve (RS-V) so that the first pressure circuit (Hl) can be supplied with hydraulic fluid by the second pressure circuit (H2). [Claim 11] Hydraulic system (HY) according to claim 10, characterized in that the valve (RS-V) is a non-return valve. [Claim 12] Hydraulic system (HY) according to one of the preceding claims, characterized in that the hydraulic system (HY) comprises an electronic control unit (ECU) intended for the control thereof. [Claim 13] Operating method of a hydraulic system (HY) according to claim 12, characterized in that the electronic control unit (ECU) regulates the pressure in the second pressure circuit (H2) according to a need for volume flow of the first pressure circuit (Hl). [Claim 14] Method according to claim 13, characterized in that the electronic control unit (ECU) regulates the pressure in the second pressure circuit (H2) as a function of the volume flow requirement of the first pressure circuit (Hl), so that that the pressure in the second pressure circuit (H2) exceeds the pressure in the first
    pressure circuit (HI) so that the pressure supply to the second pressure circuit (H2) is carried out by the second pump (MP).
    [Claim 15] Double clutch gearbox (G) for a motor vehicle powertrain, characterized by a hydraulic system (HY) according to one of claims 1 to 12.
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    同族专利:
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    法律状态:
    2020-07-15| PLFP| Fee payment|Year of fee payment: 2 |
    2021-07-14| PLFP| Fee payment|Year of fee payment: 3 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102018214427.3A|DE102018214427A1|2018-08-27|2018-08-27|Hydraulic system for a double clutch transmission|
    DE102018214427.3|2018-08-27|
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