阅读说明：本技术 用于双离合器变速器的液压系统 (Hydraulic system for a dual clutch transmission ) 是由 A·哈伯施托克 T·施密特 于 2019-08-22 设计创作，主要内容包括：本发明涉及一种用于机动车动力总成系统的双离合器变速器(G)的液压系统(HY),其中,该液压系统(HY)具有用于对第一压力回路(H1)进行压力供应的第一泵(EP)和用于对第二压力回路(H2)进行压力供应的第二泵(MP),所述第一压力回路(H1)至少用于液压操纵双离合器变速器(G)的双离合器,并且所述第二压力回路(H2)至少用于润滑双离合器变速器的其它组件,所述第一泵(EP)能够由仅配设给第一泵(EP)的电动机(EM1)驱动,该电动机不是设置用于驱动机动车,其中,所述第二泵(MP)能够由机动车动力总成系统的驱动单元驱动。本发明还涉及一种用于运行所述液压系统的方法以及一种具有所述液压系统的双离合器变速器(G)。(The invention relates to a hydraulic system (HY) for a dual clutch transmission (G) of a motor vehicle drive train, wherein the hydraulic system (HY) has a first pump (EP) for pressure supply of a first pressure circuit (H1) and a second pump (MP) for pressure supply of a second pressure circuit (H2), the first pressure circuit (H1) being used at least for hydraulically actuating a dual clutch of the dual clutch transmission (G) and the second pressure circuit (H2) being used at least for lubricating other components of the dual clutch transmission, the first pump (EP) being drivable by an electric motor (EM1) which is assigned exclusively to the first pump (EP) and which is not provided for driving the motor vehicle, wherein the second pump (MP) is drivable by a drive unit of the motor vehicle drive train. The invention also relates to a method for operating the hydraulic system and to a dual clutch transmission (G) having the hydraulic system.)

1. A hydraulic system (HY) for a dual clutch transmission (G) of a motor vehicle drive train, wherein the hydraulic system (HY) has a first pump (EP) for pressure supply of a first pressure circuit (H1) and a second pump (MP) for pressure supply of a second pressure circuit (H2),

wherein the first pressure circuit (H1) is provided at least for hydraulically actuating a double clutch (K1, K2) of a double clutch transmission (G), and the second pressure circuit (H2) is provided at least for lubricating further components of the double clutch transmission (G),

characterized in that the first pump (EP) can be driven by an electric motor (EM1) which is assigned exclusively to the first pump (EP) and which is not provided for driving the motor vehicle, wherein the second pump (MP) can be driven by a drive unit (VM, EM2) of the motor vehicle drive train.

2. The hydraulic system (HY) as set forth in claim 1 characterized in that the first pressure circuit (H1) is not provided with other consumers other than dual clutch operation.

3. The hydraulic system (HY) according to claim 1, characterized in that the first pressure circuit (H1) is provided for actuating a separating clutch (K0) between two drive units (VM, EM2) of a motor vehicle drive-train, wherein the first pressure circuit (H1) is not assigned further consumers than the double clutch actuation and the hydraulic actuation of the separating clutch (K0).

4. The hydraulic system (HY) as claimed above characterized in that the second pressure circuit (H2) provides an actuator (ST1, ST2) for operating the shifting clutches of a dual clutch transmission (G).

5. Hydraulic system (HY) according to the preceding claims characterised in that the output of the first pump (EP) is directly connected to the first pressure circuit (H1) where the pressure in the first pressure circuit (H1) can be regulated by speed control of the electric motor (EM1) assigned to the first pump (EP).

6. Hydraulic system (HY) according to any of claims 1 to 4 characterized in that the output of the first pump (EP) is connected to the first pressure circuit (H1) via a pressure limiting valve (DB-V1) where the pressure limiting valve (DB-V1) is pre-controlled or regulated to an invariable limit pressure.

7. Hydraulic system (HY) according to any of the previous claims characterised in that the second pump (MP) is implemented as a fixed displacement pump.

8. The hydraulic system (HY) according to any of claims 1-6 characterized by that the second pump (MP) is implemented as a variable displacement pump.

9. Hydraulic system (HY) according to any of claims 1 to 8 characterized in that the output of the second pump (MP) is connected to the second pressure circuit (H2) via a second pressure limiting valve (DB-V2) where the second pressure limiting valve (DB-V2) is pre-controlled by means of a pressure control valve (EDS _ MOP).

10. Hydraulic system (HY) according to any of the claims where the first and second pressure circuits (H1, H2) are interconnected by valves (RS-V) so that the first pressure circuit (H1) can be supplied with hydraulic fluid through the second pressure circuit (H2).

11. The hydraulic system (HY) of claim 10 wherein the valve (RS-V) is a check valve.

12. Hydraulic system (HY) according to the previous claims characterised in that it has an Electronic Control Unit (ECU) for controlling the hydraulic system.

13. A method for operating the hydraulic system (HY) according to claim 12, characterized in that the control unit (ECU) regulates the pressure in the second pressure circuit (H2) as a function of the volume flow demand of the first pressure circuit (H1).

14. The method as claimed in claim 13, characterized in that the control unit (ECU) adjusts the pressure in the second pressure circuit (H2) as a function of the volume flow requirement of the first pressure circuit (H1) in such a way that the pressure in the second pressure circuit (H2) exceeds the pressure in the first pressure circuit (H1), so that the pressure supply of the second pressure circuit (H2) is effected by the second pump (MP).

15. A double clutch transmission (G) for a motor vehicle drive train, characterized in that a hydraulic system (HY) according to any one of claims 1 to 12 is provided.

Technical Field

The invention relates to a hydraulic system for a dual clutch transmission of a motor vehicle powertrain system. The invention also relates to a dual clutch transmission having such a hydraulic system, and to a method for operating such a hydraulic system.

Background

A hydraulic control for a dual clutch transmission is known, for example, from DE102014216648a 1. In one embodiment, the hydraulic energy source of the control device comprises a first hydraulic pump and a second hydraulic pump. The first hydraulic pump can be driven by the internal combustion engine and is used for pressure supply to a high-pressure circuit, through which the double clutch can be actuated. The second hydraulic pump can be driven by means of an electric motor and is used to supply a cooling circuit. In a further embodiment, the two hydraulic pumps can be driven both by the internal combustion engine and by the electric machine.

The control known in the prior art offers the following advantages: not all the pressure oil for the cooling circuit has to be led out of the high-pressure circuit. The pressure oil required for the high-pressure circuit, which is generated by the first pump driven by the internal combustion engine, can nevertheless continue to be adjusted to the required quantity.

Disclosure of Invention

The object of the present invention is to provide a hydraulic system for a dual clutch transmission, which is characterized by a low energy requirement.

This object is achieved by the features of claim 1. Advantageous embodiments emerge from the dependent claims, the description and the drawings. Furthermore, a method for controlling is specified in claim 13.

A hydraulic system for a dual clutch transmission of a motor vehicle powertrain system is presented. The hydraulic system has a first pump for pressure supply of the first pressure circuit and a second pump for pressure supply of the second pressure circuit. The first pump is provided at least for hydraulically actuating a double clutch of the double clutch transmission, while the second pump is provided at least for lubricating other components of the double clutch transmission.

According to the invention, the first pump can be driven by its own electric motor. The electric motor is independent of the drive of the motor vehicle and is used only to drive the first pump. The second pump can preferably be driven by a drive unit of the drive train of the motor vehicle, i.e. for example by an internal combustion engine, and/or by an electric motor provided for driving the motor vehicle.

Since the pressure supply of the dual clutch transmission takes place via the first pump driven by the electric motor, the volume flow requirement of the first pressure circuit can be met independently of the rotational speed range of the internal combustion engine. If the double clutch is not actuated, the leakage oil requirement of the first pressure circuit is only to be met, for which only a small energy consumption is required. For the pressure supply of the lubrication, only a small pressure is required compared to the maximum requirement of the first pressure circuit, so that the power consumption of the second pump is relatively small.

Preferably, the first pressure circuit is not assigned any other hydraulic consumers than the double clutch actuation device. Due to the small number of consumers, the leakage oil requirement of the first pressure circuit is also small.

If the dual clutch transmission is part of a hybrid drive-train, a disconnect clutch is often provided between the powerplants of the hybrid drive-train. Such a hybrid drive train is known, for example, from DE102010003442a 1. Preferably, the hydraulic actuation device of the separating clutch is also assigned to the first pressure circuit, wherein the dual clutch actuation device and the separating clutch actuation device are the only consumers of the first pressure circuit. The hydraulic demand of the separator clutch actuation device and the hydraulic demand of the dual clutch actuation device are very similar, so that it is advantageous to integrate the separator clutch actuation device in the first pressure circuit. Since all other hydraulic consumers are supplied by the second pressure circuit, the leakage oil demand to be met by the first pump continues to be small.

As is generally known, in order to form the gears of the dual clutch transmission, in addition to the dual clutch, shifting clutches are also actuated, which are assigned to the partial transmissions of the dual clutch transmission. The shifting clutch is usually designed as a dog clutch and can be actuated, for example, by a shifting roller or a shifting lever. The actuation can be performed hydraulically or electromechanically, for example. When the shifting clutch is hydraulically actuated, the actuated pressure supply is preferably carried out via a second pressure circuit. Since the dog clutch requires operating energy only for engagement or disengagement, but no or only a small amount of operating energy is required to maintain the engaged or disengaged state. In contrast, dual clutches are usually designed as power-shiftable diaphragm clutches, which are intended to be supplied with actuating energy at all times in order to maintain a closed state, for example, when they are designed as normally open clutches. The assignment of the shifting clutch actuator to the second pressure circuit therefore promotes the energy efficiency of the hydraulic system.

According to one possible embodiment, the pressure output of the first pump is connected directly to the first pressure circuit. In other words, no valve designed for pressure reduction or pressure limitation is provided between the pressure output of the first pump and the first pressure circuit. However, a shut-off valve can be provided which prevents a return flow of hydraulic fluid from the second pressure circuit to the pressure outlet of the first pump. The pressure in the first pressure circuit can be adjusted accordingly by controlling the rotational speed of the electric motor driving the first pump. This configuration of the hydraulic system is particularly energy efficient, since there is no need to regulate the output pressure of the first pump. A pressure sensor may be used to detect the pressure in the first pressure circuit. Instead, the pressure in the first pressure circuit can be evaluated using a pressure model which describes the relationship between the power of the electric motor, the temperature of the hydraulic fluid, the volumetric flow rate consumption of the hydraulic consumer and the expected leakage.

According to an alternative possible embodiment, the pressure output of the first pump is connected to the first pressure circuit via a pressure-limiting valve. The pressure limiting valve may be pre-controlled or regulated to an unchangeable limit pressure. If the pressure in the first pressure circuit reaches a limit pressure that is not variable or variable by a pilot control, the output of the first pump is connected to a tank of the hydraulic system or to the suction connection of the first pump. This configuration of the hydraulic system reduces the control or regulation effort of the first pump.

Preferably, the second pump is embodied as a fixed displacement pump, i.e. as a pump having a delivery volume that is not variable at a constant rotational speed. The use of such a pump is particularly cost effective without significantly affecting the energy efficiency of the hydraulic system. Alternatively, the second pump can be embodied as a variable displacement pump, i.e. as a pump having a controllably variable delivery volume at constant rotational speed. This solution will further improve the energy efficiency of the hydraulic system.

Preferably, the output of the second pump is connected to the second pressure circuit via a second pressure-limiting valve, wherein the second pressure-limiting valve is pre-controlled by means of a pressure control valve. Whereby the pressure in the second pressure circuit can be raised or lowered as desired.

The first pressure circuit and the second pressure circuit are preferably connected to one another by a valve, particularly preferably by a check valve, in such a way that a consumer of the first pressure circuit can be supplied with hydraulic fluid via the second pressure circuit. By means of this embodiment, the maximum required volume flow of the first pump can be kept low by: in the event of a high volume flow requirement of the first pressure circuit, the first pressure circuit is supplied by the second pump. This situation is usually only of short duration and therefore only slightly impairs the energy efficiency of the hydraulic system.

The hydraulic system may be provided with an electronic control unit which receives the signal of at least one sensor, is connected in communication with other control units and controls the actuators of the hydraulic system on the basis of the signal of the at least one sensor and on the basis of other signals and information.

The invention also relates to a method for operating the hydraulic system described above, according to which the control unit regulates the pressure in the second pressure circuit according to the volume flow requirement of the first pressure circuit. For this purpose, for example, pressure control valves can be used. The control unit can increase the pressure in the second pressure circuit to such an extent that it exceeds the pressure in the first pressure circuit, so that the consumer of the first pressure circuit is supplied with hydraulic fluid by the second pump instead of the first pump.

The invention also relates to a dual clutch transmission for a motor vehicle drive train having the aforementioned hydraulic system. Furthermore, the double clutch transmission can have an electric motor, which is provided for driving the motor vehicle. The dual clutch transmission may include a disconnect clutch disposed in the power flow between the internal combustion engine of the powertrain system and the dual clutch of the dual clutch transmission.

Drawings

Embodiments of the invention are explained in detail below with the aid of the figures. Wherein:

FIG. 1 shows a schematic diagram of a dual clutch transmission; and

fig. 2 to 5 each show a circuit diagram of a different exemplary embodiment of a hydraulic system according to the invention.

Detailed Description

Fig. 1 shows a schematic representation of a dual clutch transmission G with a hydraulic system HY. The motor vehicle transmission G has a connecting shaft AN, which can be connected to a drive shaft GW1 via a disconnect clutch K0. The internal combustion engine VM is connected to the connecting shaft AN. The rotor of the electric machine EM2 is connected to the drive shaft GW 1. The dual clutch transmission G has a clutch section GK which accommodates a first clutch K1 and a second clutch K2. The two clutches K1, K2 form a dual clutch. By closing the first clutch K1, the drive shaft GW1 can be connected to the first subtransmission. By closing the second clutch K2, the drive shaft GW1 can be connected to the second subtransmission. In the shifting range GW, a plurality of different gears can be formed between the subtransmission and the output shaft GW2 by means of a gear train, not shown. The gears are engaged or disengaged by means of two shift cylinders ST1, ST 2.

The pressure supply of the hydraulic system HY is effected by the first pump EP and the second pump MP. The first pump EP is driven by an electric motor EM1 which is assigned exclusively to the first pump EP. The second pump MP is driven by a drive shaft GW1, which is driven by the electric machine EM2 or by the internal combustion engine VM when the disconnect clutch K0 is closed. The two pumps EP, MP pump hydraulic fluid from a tank T of the hydraulic system HY and deliver the hydraulic fluid to consumers of the hydraulic system HY. The twin-clutch transmission G has an electronic control unit ECU which is at least designed to control the hydraulic system HY.

The structure of the dual clutch transmission G shown in fig. 1 is to be regarded as exemplary only. The dual clutch transmission G can also be implemented without the electric machine EM2 and without the separating clutch K0, so that the internal combustion engine VM is permanently connected to the driveshaft GW 1.

Fig. 2 shows a circuit diagram of the hydraulic system HY according to the first embodiment of the present invention. The hydraulic system HY has a first pressure circuit H1 and a second pressure circuit H2. The first pressure circuit H1 is provided for actuating the two clutches K1, K2 of the dual clutch and for actuating the separating clutch K0. Each of the clutches K1, K2, K0 is assigned a pressure control valve VK1, VK2, VK 0. The pressure in the first pressure circuit H1 can be set to a desired level for actuating the respective clutch K1, K2, K0 by means of the pressure control valves VK1, VK2, VK 0. If the dual clutch transmission G does not disconnect the clutch K0, the pressure control valve VK0 is correspondingly eliminated.

The second pressure circuit H2 is separated from the first pressure circuit H1 by a valve RS-V, and illustratively has three consumer circuits H2_ KS, H2_ AK, and H2_ DI. The consumer circuit H2_ KS serves to cool and lubricate the dual clutch transmission G. The consumer circuit H2_ AK is used to actuate the shift cylinders ST1, ST2, by means of which the shifting clutches of the dual clutch transmission G are actuated. The only optionally present consumer circuit H2 — DI is used, for example, for actuating a central synchronizer of the dual clutch transmission G, if such a central synchronizer is provided.

The first pressure circuit H1 is directly connected to the output of the first pump EP, so that the output pressure of the first pump EP directly determines the pressure in the first pressure circuit H1. By controlling the rotational speed of the first pump EP, the pressure in the first pressure circuit H1 can be adjusted accordingly. The second pressure circuit H2 is connected with the second pump MP via a pressure-limiting valve DB-V2. The output of the second pump MP is connected to the suction connection of the second pump MP if the output pressure of the second pump MP reaches or exceeds a limit value. The limit values relate to the spring prestress of the pressure limiting valve DB-V2 and to the pilot control force which can be set by the pressure control valve EDS _ MOP.

Fig. 3 shows a circuit diagram of a hydraulic system HY according to a second exemplary embodiment of the present disclosure, in which a pressure-limiting valve DB-V1 is arranged between the output of the first pump EP and the first pressure circuit H1. If the output pressure of the first pump EP reaches or exceeds a limit value, the output of the first pump EP is connected to the suction connection of the first pump EP. This limit value is related to the spring prestress of the pressure limiting valve DB-V1 and to the pilot control force which can be set by the pressure control valve EDS _ EOP.

Fig. 4 shows a circuit diagram of a hydraulic system HY according to a third embodiment of the invention, which hydraulic system substantially corresponds to the second embodiment shown in fig. 3. The pressure control valve EDS _ EOP is now cancelled, so that the pressure limiting valve DB-V1 is set to the non-variable limit pressure.

Fig. 5 shows a circuit diagram of a hydraulic system HY according to a fourth embodiment of the invention, which hydraulic system substantially corresponds to the third embodiment shown in fig. 4. The second pump MP is now implemented as a variable displacement pump, i.e. as a pump with a controllably variable delivery volume at constant rotational speed. This configuration of the second pump MP is also possible in other embodiments of the hydraulic system HY.

In all embodiments of the hydraulic system HY, the consumers of the first pressure circuit H1 have a high pressure requirement and a small volume flow requirement. Due to the small 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 requires only a small pressure, for which an increased volume flow is required compared to the first pressure circuit H1. Due to the small pressure, the drive power of the second pump MP to be applied to the consumer circuit H2_ KS is low. If the consumer circuits H2_ AK, H2_ DI of the second pressure circuit H2 require a higher pressure, the pressure in the second pressure circuit H2 may be increased by controlling the pressure control valve EDS _ MOP for the required duration.

Due to the connection of the two pressure circuits H1, H2 via the valves RS-V, the delivery volume flow of the first pump EP can be kept small. When the volumetric flow demand of the consumers of the first pressure circuit H1 then increases, for example during a gear change of the dual clutch transmission G, the supply of the first pressure circuit H1 can be effected by the second pump MP as required. For this purpose, the pressure control valve EDS _ MOP is actuated such that the pressure in the second pressure circuit H2 is higher than the pressure in the first pressure circuit H1. Thereby, the valve RS-V constructed as a check valve is automatically opened. If the hydraulic system HY has the pressure-limiting valve DB-V1, the limit pressure of the pressure-limiting valve DB-V1 is either selected or, by means of the pressure control valve EDS _ EOP, the limit pressure of the pressure-limiting valve DB-V1 is set in such a way that, in the operating state, no connection is established from the second pressure circuit H2 via the pressure-limiting valve DB-V1 to the suction connection of the first pump EP. After the end of the shifting operation, the pressure in the second pressure circuit H2 is reduced again by correspondingly controlling the pressure control valve EDS _ MOP, so that the first pump EP takes over again the supply of the first pressure circuit H1.

List of reference numerals

G double clutch transmission

VM internal combustion engine

AN connecting shaft

K0 disconnect clutch

EM2 motor

GW1 drive shaft

GW2 driven shaft

GG derailleur casing

GK clutch segment

K1, K2 double clutch

GW shift segment

ST1, ST2 Shift Cylinder

ECU electronic control unit

HY hydraulic system

EP first pump

EM1 motor

MP second pump

T-shaped oil tank

H1 first pressure circuit

H2 second pressure loop

VK1 pressure control valve

VK2 pressure control valve

VK0 pressure control valve

RS-V valve

DB-V1 pressure limiting valve

EDS _ EOP pressure control valve

DB-V2 pressure limiting valve

EDS _ MOP pressure control valve

H2_ KS consumer loop

H2_ AK consumer loop

H2_ DI consumer loop