CN109236890B

CN109236890B - Method and system for fluid control of two partial clutches

Info

Publication number: CN109236890B
Application number: CN201810620971.4A
Authority: CN
Inventors: 卡斯滕·迈耶; 马可·格雷特
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2017-07-11
Filing date: 2018-06-15
Publication date: 2022-07-01
Anticipated expiration: 2038-06-15
Also published as: CN109236890A; DE102017115453A1

Abstract

The invention relates to a method and a system for the fluidic control of two partial clutches (15, 16), which belong to a dual clutch transmission, wherein the two partial clutches are controlled by means of two pump actuators (11, 12) in a fluidic system (10). In order to improve the functionality and/or the availability when controlling the two partial clutches (15, 16), the two secondary fluid application devices (18, 19) are simultaneously controlled, if necessary, by means of the two pump actuators (11, 12).

Description

Method and system for fluid control of two partial clutches

Technical Field

The invention relates to a method and a system for fluid control of two partial clutches of a dual clutch transmission by means of two pump actuators.

Background

From german laid-open patent application DE 102015218784 a1 a fluid device for fluid control of motor vehicle components is known, wherein at least one motor vehicle component is a clutch and at least one further motor vehicle component is a transmission component, wherein the fluid device has a plurality of fluid sources, and each of the fluid sources comprises a fluid pump having a first delivery direction and a second delivery direction opposite to the first delivery direction, wherein the fluid sources are fluidically connected in the fluid device in such a way that at least one of the fluid sources is suitable for actuating two of the motor vehicle components and at least one of the fluid flow sources is suitable for a motor vehicle component which can also pass the further fluid source.

Disclosure of Invention

The object of the invention is to improve the functionality and/or the availability in the control of the two partial clutches of a dual clutch transmission by means of two pump actuators in a fluid system.

The object is achieved by a method for the fluidic control of two partial clutches of a dual clutch transmission by means of two pump actuators in a fluidic system, wherein two secondary fluid application devices are simultaneously controlled by the two pump actuators if necessary. The pump actuators are preferably electrical pump actuators, each comprising a fluid pump, in particular a hydraulic pump, driven by an electric motor. The electric motor is controlled to selectively actuate one of the split clutch or the secondary fluid application device. The fluid pump, in particular the hydraulic pump, is designed as a reversible pump which can deliver a fluid, in particular a hydraulic medium, in opposite delivery directions. The pump actuator is assigned to the two partial clutches. The valves, each having a tank connection, are connected parallel to the actuator. Advantageously, the or valve is connected between the two pump actuators and the secondary application device. The two secondary pump actuators can be used very effectively for actuating the two secondary fluid application devices, in addition to controlling the two partial clutches, for example via actively actuatable valve devices, by suitable connection of the pump actuators to the two secondary fluid application devices. An advantage of such a design is that the own actuator for the secondary fluid application device can be completely dispensed with.

A preferred embodiment of the method is characterized in that the two secondary fluid application devices are a fluid transmission control system and an additional disconnect clutch. The fluid type transmission control system includes, for example, a hydraulic or pneumatic shift regulator or a hydraulic or pneumatic transmission actuator. Advantageously, the two partial transmissions of the dual clutch transmission are controlled by a fluid transmission control system. The additional separating clutch is, for example, the K0 clutch in a hybrid drive train having a primary drive and a secondary drive. The main drive is, for example, a heat engine, which is also referred to as an internal combustion engine. The secondary drive is, for example, an electric drive comprising at least one electric motor or an electric motor. An additional separating clutch is preferably arranged between the primary drive and the secondary drive. The main drive can be disconnected by an additional separating clutch, in order to allow a motor vehicle equipped with a hybrid drive train to be driven exclusively by the secondary drive, for example a pure electric drive.

A further preferred embodiment of the method is characterized in that the two secondary fluid application means are controlled independently of each other by one of the pump actuators. Thus, for example, a pump actuator of a currently uncontrolled partial clutch of a dual clutch transmission can be used to control one of the secondary fluid application devices. However, depending on the design of the hydraulic system, it is also possible to use two pump actuators simultaneously in order to actuate two secondary fluid application devices independently of one another.

A further preferred embodiment of the method is characterized in that one of the partial clutches is kept in the current state for a period of time, so that two pump actuators can be used for two secondary fluid application devices during said period of time. For example, the disconnect coupling, which remains in its current state, is fluidly disconnected from the fluid system. Disconnection of the partial clutch from the fluid system is effected, for example, by means of a suitable valve device which interrupts the fluid connection between the partial clutch and the pump actuator to which the partial clutch is assigned.

A further preferred embodiment of the method is characterized in that the leakage occurring during the holding of the partial clutch is compensated for by a short-term fluid connection of the associated pump actuator. Leakage itself is undesirable, but is generally unavoidable. If the clutch pressure drops too much, fluid, in particular hydraulic medium, is replenished by the associated pump actuator in order to keep the partial clutch in its current state.

A further preferred embodiment of the method is characterized in that it will be more frequent during operation of the dual clutch transmission

The partial clutches of the partial transmissions used are fluidically disconnected from the fluid system and are fluidically connected only to the associated pump actuators, as required. In this exemplary embodiment, the separating clutch is only fluidically connected to a further separating clutch for the purpose of control. During the remaining time, the pump actuator can be used together with a further pump actuator to control a secondary fluid application or to supply a fluid, in particular a hydraulic medium.

In a fluid system having two pump actuators for fluid control of two partial clutches of a dual clutch transmission, which comprises two partial transmissions, by means of which gears in the dual clutch transmission are realized, in particular according to the method described above, the above-mentioned technical problem is alternatively or additionally solved in that an actively actuatable valve device is arranged between the two pump actuators and two secondary fluid application devices, in particular between the two secondary fluid application devices described above. As is known from german patent document DE 102015218784 a1, an active valve device replaces a passive or valve in, for example, a conventional fluid system or a conventional fluid device. In this case, it is known that active valve arrangements are subject to increased control costs compared to passive or valves.

A preferred embodiment of the fluid system is characterized in that the actively controllable valve means is designed as a two-position four-way valve. The two-position four-way valve includes interfaces for two secondary fluid applications, respectively. One of the secondary fluid applications, such as the fluid control system, can be directly connected to the two-position, four-way valve. A further secondary fluid application device, such as an additional disconnect clutch or a K0 clutch, is preferably connected to the two-position four-way valve with the interposition of a further shutoff valve. The further shut-off valve is preferably designed as a two-position, two-way valve with an open position and a closed position. Advantageously, the additional shut-off valve is preloaded into its closed position, in which the connection between the two-position four-way valve and the secondary fluid application device (for example the additional separating clutch or the K0 clutch) is interrupted. The shut-off valve can be switched from its closed position to its open position by electromagnetic actuation. By means of the valve device being designed as a two-position four-way valve, it is possible to control the two secondary fluid application devices simultaneously and in accordance with the switching position of each of the two pump drives. In particular, the combination of the shut-off valve described below between one of the separating clutches and the associated pump actuator enables a valve device designed as a two-position four-way valve to simultaneously control two secondary fluid application devices, so that a significant usability and time advantage is achieved in motor vehicles equipped with such a fluid system. Preferably, the actively controllable valve device is electromagnetically controlled. The shut-off valve corresponding to one of the secondary fluid application devices is also referred to as a shut-off valve.

A further preferred embodiment of the fluid system is characterized in that the actively controllable valve means is designed as a four-position, four-way valve. Preferably, the actively controllable valve device is electromagnetically controlled. In the design as a four-position four-way valve, the previously described shut-off function by means of an additional shut-off valve is integrated into the actively controllable valve device. With a four-position four-way valve, the following four functions are advantageously achieved. The K0 clutch, which is one of the secondary fluid applications, is blocked to reduce leakage and the fluid transmission control system and the first pump actuator, which are the other secondary fluid applications, are connected. The K0 clutch is blocked to reduce leakage and the fluid transmission control system is connected with the second pump actuator. The K0 clutch is connected to the first pump actuator, and the fluid transmission control system is connected to the second pump actuator. The K0 clutch and the second actuator are connected, and the fluid transmission control system is connected with the first pump actuator.

In a particularly preferred embodiment of the actively controllable valve device designed as a four-way valve, in a dedicated fluid-type transmission control device, it is not necessary to adjust the valve device to a switching position in which it is disconnected from the K0 clutch, in which switching position pressurized fluid of the K0 clutch can escape. Thus, the fluid transmission control system can be connected with the first and second pump actuators without creating additional leakage at the K0 clutch.

A further preferred embodiment of the fluid system is characterized in that the actively controllable valve device is designed as a rotary valve. The rotary valve comprises a rotary disc which can be driven, for example, by a stepper motor and hydraulically. The advantage of the rotary disk is that an increased tightness of the interface can be achieved, so that the K0 clutch can be engaged. The pressure on the K0 clutch enables the pressure of the rotary disk for sealing by means of a corresponding active surface. In this case, however, it must be ensured that the respective pressure chamber is leak-free on the active surface, for example by using a suitable membrane.

A further preferred embodiment of the fluid system is characterized in that a shut-off valve is arranged between at least one of the partial clutches and the associated pump actuator. The shut-off valve is preferably arranged between the separating clutch and the associated pump actuator. The shut-off valve is preferably designed as a two-position, two-way valve with an open position and a closed position. In the open position, a fluid connection is made between the disconnecting coupling and the associated pump actuator. In the closed position, the fluid connection is interrupted by the shut-off valve so that the disconnecting clutch remains in the current state.

A further preferred embodiment of the fluid system is characterized in that the shut-off valve is pretensioned in its closed position. Thus, when the shut-off valve is not controlled, the partial clutch is fluidly disconnected. Thereby, the decoupler remains in its actuated state, i.e. open or closed, irrespective of unavoidable leakage. The shut-off valve is preferably electromagnetically controlled, i.e. switched from its closed position to its open position.

The hydraulic pump of the pump actuator can be designed as a vane pump, gear pump or piston pump. Advantageously, an electric motor is used to drive the pump actuator. In the first conveying direction, a pump actuator, also referred to as a reversible pump actuator, can be used, for example, to control the partial clutch, in particular to engage the partial clutch. In the second conveying direction, a reversible pump actuator can be used to control the secondary fluid application device or to supply the hydraulic medium. The clutches of the double clutch can be controlled directly or indirectly. The partial clutch can be a wet or dry clutch.

The invention also relates to a valve device and/or a shut-off valve for a fluid system as described above. The valve device and/or the shut-off valve can be operated separately.

The invention also relates to an assembly having fluidic components and/or electrical or electromechanical components for forming the above-described fluidic system, if necessary. The assembly includes, for example, a pump actuator, a valve arrangement, a shut-off valve, and various fluid application devices.

Drawings

Further advantages, technical features and details of the invention are given in the following by different embodiments which are explained in detail in connection with the figures. The attached drawings are as follows:

FIG. 1 is a fluid system having two pump actuators for fluidly controlling two partial clutches of a dual clutch transmission having an active valve arrangement configured as a two-position, four-way valve;

FIG. 2 is an active valve assembly designed as a four-position, four-way valve;

FIG. 3 is a longitudinal cross-sectional view of the structural design of a four-position four-way valve;

FIG. 4 is a fluid system having two pump actuators for fluidly controlling two partial clutches of a dual clutch transmission having an active valve arrangement according to FIG. 2; and

fig. 5 is a fluid system with two pump actuators for fluid control of two partial clutches of a dual clutch transmission with an active valve arrangement designed as a rotary valve.

Detailed Description

In fig. 1, a fluid system 10 having a first pump actuator 11 and a second pump actuator 12 is shown. The pump actuators 11, 12 are designed as reversible pump actuators. The

reversible pump actuators

11, 12 are designed as fluid pumps, in particular hydraulic pumps, which can be operated in opposite conveying directions, as indicated by the arrow symbols. The

reversible pump actuators

11 and 12 can control the double clutch 14 and the two secondary

fluid application devices

18, 19 in an advantageous manner.

The dual clutch 14 comprises a first partial clutch 15 and a second partial clutch 16. The first partial clutch 15 of the double clutch 14 can be controlled by the pump actuator 11. The second partial clutch 16 of the dual clutch 14 can be controlled by the pump actuator 12.

The two

pump actuators

11, 12 are each assigned a

valve

21, 22. The and

valves

21, 22 are also referred to as double pressure valves and have two connections, by means of which the and

valves

21, 22 are connected to corresponding connections of the associated

pump actuators

11, 12. The

valves

21, 22 include a tank port as a third port.

In a simple manner, the

valve

21, 22 or the dual pressure valve can be used to: different control situations can be established by the

pump actuators

11, 12 independently of the direction of rotation.

An electric drive for the pump actuator 11 is indicated by a rectangular symbol 23. A local control unit, for example, for adjusting the pressure, for the electric drive 23 of the pump actuator 11 is indicated by a rectangular symbol 24.

An electric drive for the pump actuator 12 is indicated by a rectangular symbol 25. A local control unit, for example, for adjusting the pressure, for the electric drive 25 of the pump actuator 12 is indicated by a rectangular symbol 26.

A shut-off valve 28 is arranged in the clutch supply line 27 of the separating clutch 16. The shut-off valve 28 is designed as a two-position, two-way valve having a closed position and an open position. The spring symbol indicates that the shut-off valve 28 is biased into its illustrated closed position.

In the closed position shown, the shut-off valve 28 interrupts the fluid connection between the pump actuator 12 and the disconnect coupling 16. If the shut-off valve 28 is actuated electromagnetically (indicated by a further symbol), the shut-off valve 28 is switched into its open position in which the fluid connection between the right-hand output of the pump actuator 12 in fig. 1 and the disconnecting clutch 16 is opened.

Or valve 30 is connected between the two

pump actuators

11 and 12 on the right side of fig. 1 and the secondary fluid application device 18 on the left side of fig. 1. The pump actuator 11 or the pump actuator 12 can supply the fluid delivery flow rate and the fluid delivery pressure to the secondary fluid application device 18 through the or valve 30.

The secondary application device 18 of fig. 1 and 5 is a fluid transmission control system. The fluid transmission control system can include a gear adjuster or a fluid actuator of the transmission. In fig. 1 and 5, the secondary application device 19 is a further disconnect clutch, which is also referred to as the K0 clutch.

As shown in fig. 1, 4 and 5, the two

secondary fluid applicators

18, 19 are coupled via an active valve arrangement 30; 40; 50 are fluidly integrated into fluid system 10. The secondary fluid application device 18 is connected to the active valve device 30 via a connecting line 34; 40; 50. the secondary fluid application device 19 is connected to the active valve device 30 via a connecting line 35; 40; 50.

the pump actuator 11 is connected to the active valve device 30 via a connecting line 37; 40; 50. the pump actuator 12 is connected to the active valve device 30 via a connecting line 36; 40; 50. two connecting

lines

36 and 37 respectively start from the fluid branches or

fluid nodes

33, 32. The fluid branches or

fluid nodes

33, 32 are each connected to the

pump actuators

12, 11 and to the

valves

22, 21 in parallel with the

pump actuators

12, 11.

With respect to the valve device 30; 40; 50, the term "active" refers to the valve arrangement 30; 40; 50 can be actively controlled. As indicated by corresponding symbols in fig. 1 and 4, the valve device 30; the actuation of 40 is electromagnetic. As shown by the rectangle in fig. 5, the actuation of the valve means 50 is done by an electric drive.

In the embodiment of the fluid system 10 shown in fig. 1, the active valve device 30 is designed as a two-position four-way valve 31. By means of the two-position four-way valve 31, the dual clutch transmission can be controlled simultaneously by the two electrically operated

pump actuators

11, 12, depending on the respective switching position of the valve device 30, by means of the secondary fluid application device 18 designed as a fluid transmission control system and the secondary fluid application device 19 designed as a K0 clutch.

A shut-off valve 38, also referred to as a shut-off valve, is also arranged in the connecting line 35 to the K0 clutch 19. The shut-off valve 38 is designed as a two-position, two-way valve having a closed position and an open position. The spring symbol indicates that the shut-off valve 38 is biased into its closed position. In the case of electromagnetic control, the shutoff valve 38 is opened.

With the fluid system 10 shown in fig. 1, the two secondary

fluid application devices

18, 19 can be controlled simultaneously, resulting in significant usability and time advantages in a motor vehicle equipped with the fluid system 10.

As shown in fig. 1, the K0 clutch 19 and the fluid system 10 can be fluidly disconnected by the shutoff valve 38. Thus, the K0 clutch 19 can remain in its current state without fluid actuation. To fluidly actuate the K0 clutch 19, the shutoff valve 38 is opened. The K0 clutch 19 can then be controlled by the active valve device 30.

As can be seen in fig. 2 and 4, the active valve device 40 is designed as a four-way valve 41. In this exemplary embodiment, the shut-off function illustrated in fig. 1 by the shut-off valve 38 is integrated into the valve device 40.

Fig. 3 shows the structural design of the valve device 40. In the illustrated construction, the valve arrangement 40 comprises a valve housing 60 with seven connections 61 to 67. The

interfaces

61 and 62 correspond to the K0 clutch (C)

18 in fig. 4). The interface 63 corresponds to the fluid transmission control system (19 in fig. 4). The interface 64 corresponds to the second pump actuator (12 in fig. 4). The interface 65 corresponds to the first pump actuator (11 in fig. 4). The interface 66 also corresponds to the first pump actuator (11 in fig. 4). The interface 67 corresponds to the second pump actuator (12 in fig. 4).

A valve piston 68 is accommodated in the valve housing 60, the valve piston 68 being movable back and forth, i.e. to the left and right in fig. 3, for example by electromagnetic control, against the biasing force of a spring. The valve piston 68 comprises a total of four piston sections with different dimensions in the axial direction.

The piston sections 71 to 74 of the valve piston 68 are dimensioned in such a way with the connections 61 to 67 of the valve device 40 that, in the case of a shift-only control of the secondary fluid application device (19 in fig. 4), there is no need to switch into an idle position, in which the connection to the K0 clutch (18 in fig. 4) is opened and thus pressurized fluid of the K0 clutch can escape. Thus, the transmission control system (19 in FIG. 4) can be connected to the first and second pump actuators without creating additional leakage at the K0 clutch.

With the active valve device 40, four functions can be advantageously achieved during operation of the fluid system 10. The fluid-type transmission control system (secondary fluid application device (19 in fig. 4)) is also abbreviated as GASS, where the capital letters GASS stands for the english term Gear Actuated Subsystem.

In a first function, to reduce leakage, the K0 clutch is disengaged or blocked, and the GASS is connected to the first pump actuator via the valve arrangement 40. In a second function, to reduce leakage, the K0 clutch is also blocked or disengaged, and the GASS is connected to the second pump actuator via the valve arrangement 40. In a third function, the K0 clutch is connected to the first pump actuator and the GASS is connected to the second pump actuator. In a fourth function, the K0 clutch is connected to the second pump actuator and the GASS is connected to the first pump actuator.

The valve device 50 shown in fig. 5 is designed as a rotary valve with a rotary disk 51. The turntable 51 is actuated via a drive device 52. The turntable 51 is electrically driven by a stepping motor, for example. However, the rotary disk 51 can also be driven fluidically, in particular hydraulically.

The advantage of the turntable 51 is that an increased tightness of the interface can be achieved. Advantageously, the K0 clutch 19 can therefore be completely engaged or disengaged. By means of corresponding active surfaces, the pressure on the K0 clutch 19 can be used in order to exert pressure on the rotary disk 51. By this pressure, a better sealing can be achieved by pressing the dial. In this case, however, it must be ensured that the pressure chamber is free of leaks at the active surface. This can be achieved, for example, by using a membrane.

List of reference numerals

10 fluid system

11 Pump actuator

12 pump actuator

14 double clutch

15 separating and combining device

16-minute clutch

18 secondary application device

19 Secondary application device

21 and a valve

22 and a valve

23 rectangular icon

24 rectangular icon

25 rectangular icon

26 rectangular icon

27 Clutch feed line

28 stop valve

30 active valve device

31 two-position four-way valve

32 branches

33 branch off

34 connecting line

35 connecting line

36 connecting pipeline

37 connecting the pipeline

38 stop valve

40 active valve device

41 four-position four-way valve

50 active valve device

51 rotating disk

52 drive device

60 valve housing

61 interface

62 interface

63 interface

64 interface

65 interface

66 interface

67 interface

68 valve piston

71 piston section

72 piston section

73 piston section

74 piston section

Claims

1. A method for fluid control of two part-clutches (15, 16) of a dual clutch transmission by means of two pump actuators (11, 12) in a fluid system (10), characterized in that two secondary fluid application devices (18, 19) can be controlled simultaneously by the two pump actuators (11, 12) respectively, and at least one of the secondary fluid application devices (18, 19) can be controlled by the two pump actuators (11, 12) respectively.

2. The method of claim 1, wherein the two secondary fluid application devices (18, 19) are a fluid transmission control system and an additional disconnect clutch.

3. Method according to claim 1, characterized in that the two secondary fluid application means (18, 19) are controlled independently of each other by one of the pump actuators (11, 12).

4. A method according to any one of the preceding claims 1-3, characterised by keeping one of the part-clutches (15, 16) in the current state for a period of time, whereby the two pump actuators (11, 12) can be used for the two secondary fluid application devices (18, 19) during the period of time.

5. A fluid system (10) with two pump actuators (11, 12) for fluid control of two partial clutches (15, 16) of a dual clutch transmission comprising two partial transmissions, by means of which gears are realized according to the method of one of the preceding claims 1 to 4, characterized in that an actively controllable valve device (30; 40; 50) is arranged between the two pump actuators (11, 12) and two secondary fluid application devices (18, 19).

6. A fluid system according to claim 5, characterised in that an actively controllable valve means (30; 40; 50) is arranged between the two aforementioned secondary fluid application means (18, 19).

7. A fluid system according to claim 5 or 6, characterised in that the actively controllable valve means (30) is designed as a two-position four-way valve (31).

8. A fluid system according to claim 5 or 6, characterised in that the actively controllable valve means (40) is designed as a four-way valve (41).

9. A fluid system according to claim 5 or 6, characterised in that the actively controllable valve means (50) is designed as a rotary valve.

10. Fluid system according to claim 5 or 6, characterised in that a shut-off valve (28) is arranged between at least one of the partial clutches (15, 16) and the associated pump actuator (11, 12).

11. Valve device (30; 40; 50) and/or shut-off valve (28; 38) for a fluid system (10) according to any one of the preceding claims 5 to 10.