Apparatus for the operation of a hydrodynamic torque converter and a therewith corresponding converter bypassing clutch of a transmission apparatus

Abstract

An apparatus operating a hydrodynamic torque converter and a corresponding converter-bypass clutch of a transmission. The apparatus having a line system, a solenoid valve and a therewith coacting variable pressure controlling valve. A valve stem assembly respectively of the solenoid valve and the pressure control valve are controllable by subjection to a pilot pressure counter to a spring arrangement. A spent flow of the torque converter is, by way of a piston chamber of the converter-bypass clutch, which chamber is subjected to hydraulic fluid pressure of the spent flow of the torque converter, by means of an operational pressure aperture valve and a relief control aperture valve of the pressure control valve, connectable to a spent flow control aperture valve of the solenoid valve. By way of the piston chamber, this spent flow communicates with the hydraulic system through the spent flow control aperture valve of the solenoid valve.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be described, by way of example, with reference to the accompanying drawings. In the description, the various embodiment examples, for the sake of clarity, employ the same reference numbers for components of like functionality. There is shown in:

FIG. 1 is a very schematic presentation of a completed drive apparatus serving as a two-line converter in the drive train of a vehicle;

FIG. 2 is a very schematic outline diagram of the inventive apparatus, by way of which a two-line converter can be operated;

FIG. 3 is a characteristic curve of a solenoid valve and a characteristic curve of a variable pressure control valve of the inventive apparatus according to FIG. 2;

FIG. 4 is a very schematic presentation of an drive apparatus designed as a three-line converter of a drive train of a vehicle;

FIG. 5 is a very schematic presentation of an inventive apparatus, by way of which a three-line converter can be operated, and

FIG. 6 is a characteristic curve for the solenoid valve and a characteristic curve of the variable pressure control valve of the inventive apparatus as presented in FIG. 5.

Claims

1-11. (canceled)

12. An apparatus (100) for operating a hydrodynamic torque converter (1) and a converter-bypass clutch (2) of a transmission apparatus, the apparatus comprising a first line system (20) having a solenoid valve (WDV) and a variable pressure control valve (WKV), a valve stem assembly (WDV_S) of the solenoid valve (WDV) and a valve stem assembly (WKV_S) of the pressure control valve (WKV) being biased by a controllable pilot pressure (p_VS) counter to a spring arrangement (WDV_F, WKV_F), each of the solenoid valve (WDV) and the pressure control valve (WKV) having a plurality of control lines (L1 to L10) connected to control aperture valves (WDV_1 to WDV_8 and respectively WKV_1 to WKV_6), the control aperture valves connect to hydraulic lines (HL3, HL4, HL6, HL8, HL9) of a hydraulic line system (22) for subjecting the torque converter (1) and the converter-bypass clutch (2) to hydraulic fluid from an area of remote ends of the control aperture valves (WDV_1 to WDV_8, WKV_1 to WKV_6) to an inlet and an outlet side of the torque converter (1) as well as to a piston chamber (27) of the converter-bypass clutch (2), by way of the piston chamber (27) of the converter-bypass clutch (2), the converter-bypass clutch (2) being pressurized by a spent flow of hydraulic fluid from the torque converter (1) through the hydraulic line system (22) using an operational control aperture valve (WKV_3) of the pressure control valve (WKV) and an internally thereto connected relief control aperture valve (WDV_2) of the pressure control valve (WDV) having a spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) and by way of the piston chamber (27), separated from the spent flow of the torque converter (1), and the spent flow of the torque converter (1) directly connecting the spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) via the hydraulic line system (22).

13. The apparatus according to claim 12, wherein a first control line (L6) of the line system (20) is connected to an input feed control aperture valve (WDV_4) of the solenoid valve (WDV), the solenoid valve (WDV) is subjected to a pressure of the piston chamber of the converter-bypass clutch (2), which contains the spent flow of hydraulic fluid from the torque converter (1), which has been directed thereto through the hydraulic line system (22) which has a relief control aperture valve (WDV_7) of the solenoid valve (WDV) and is blocked by the spent flow of the torque converter (1), and the spent flow of the torque converter (1) is separated from the hydraulic line system (22) in piston chamber of the torque converter (1).

14. The apparatus according to claim 13, wherein the input feed control aperture valve (WDV_4) of the solenoid valve (WDV), by a position of the valve stem assembly (WDV_S) of the solenoid valve (WDV), the connection between the relief control aperture valve (WDV_2) and the operational control aperture valve (WDV_3) of the solenoid valve (WDV) is blocked and, upon a simultaneous valve stem blocking operation, the connection of the spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) is shut off such that the relief aperture valve (WDV_7) of the solenoid valve (WDV) is connection with the spent flow control aperture valve (WDV_6) of the solenoid valve (WDV).

15. The apparatus according to claim 13, wherein a second control line (L7) in the line system (20) is connected to the input control aperture valve (WDV_4) of the solenoid valve (WDV) is blocked by way of the piston chamber (27), and the piston chamber (27) is separated from the spent flow from the torque converter (1) of the converter-bypass clutch (2) in the area of the hydraulic line system (22).

16. The apparatus according to claim 12, wherein a control line (L8) of the line system (20) communicates with a hydraulic fluid reservoir (28) via the hydraulic line system (22) and effected by a relief control aperture valve (WKV_2) of the pressure control valve (WKV), the pressure control valve (WKV) communicates with the piston chamber (27) of the converter-bypass clutch (2) and the piston chamber (27) is separated from the spent flow of the torque converter (1).

17. The apparatus according to claim 12, wherein the operational control aperture valve (WKV_3) of the variable pressure control valve (WKV) is connected with a spent flow aperture (WKV_5) of the pressure control valve(WKV) via the line system (20) such that a pressure is applied on the valve stem (WKV_S) of the pressure control valve (WKV), the pressure applied on the valve stem (WKV_S) of the pressure control valve (WKV) is counter to the pilot pressure (p_VS) applied on the valve stem (WKV_S) of the pressure control valve (WKV) via a pilot pressure control aperture valve (WKV_1) of the variable pressure valve (WKV).

18. The apparatus according to claim 12, wherein, the operational aperture valve (WKV_3) of the variable pressure control valve (WKV) communicates with the relief control aperture valve (WKV_2) of the variable pressure control valve (WKV) when communication between an inlet feed control aperture (WKV_4) of the variable pressure control valve (WKV) and the operational aperture valve (WKV_3) of the variable pressure control valve (WKV) is blocked by the valve stem assembly (WKV_S) of the pressure control valve (WKV).

19. The apparatus according to claim 18, wherein the communication between the operational aperture valve (WK3_3) of the variable pressure control valve (WKV) and the relief control aperture valve (WKV_2) of the variable pressure control valve (WKV) is blocked by way of the valve stem (WKV_S) of the variable pressure control valve (WKV) when a position of the valve stem assembly (WKV_S) of the pressure control valve (WKV) enables communication between the inlet feed aperture valve (WKV_4) of the variable pressure control valve (WKV) and the operational aperture valve (WKV_3) of the variable pressure control valve (WKV).

20. The apparatus according to claim 12, wherein the solenoid valve (WDV) has a lubrication and cooling control aperture valve (WDV_5) which supplies a lubrication and cooling oil circulation system (14) of the transmission apparatus, the lubrication and cooling oil circulation system (14) is located downstream of the solenoid valve (WDV), and the cooling control aperture valve (WDV_5) of the solenoid valve (WDV) communicates with the lubrication and cooling circulation system (14) via the line system (20).

21. The apparatus according to claim 20, wherein the spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) communicates with the relief control aperture valve (WDV_7) of the solenoid valve (WDV) when, because of a position of the valve stem assembly (WDV_S) of the solenoid valve (WDV), the communication between the relief control aperture valve (WDV_2) of the solenoid valve (WDV) and the operational aperture valve (WDV_3) of the solenoid valve (WDV) is blocked, and the spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) communicates with the cooling control aperture valve (WDV_5) when, because of a position of the valve stem assembly (WDV_S) of the solenoid valve (WDV), the communication between the relief control aperture valve (WDV_2) of the solenoid valve (WDV) and the operational aperture valve (WDV_3) of the solenoid valve (WDV) is open.

22. The apparatus according to claim 16, wherein the relief aperture valve (WDV_7) of the solenoid valve (WDV) communicates with the hydraulic fluid reservoir (28), an auxiliary pressure control valve (11), located between the relief aperture valve (WKV_2) and the hydraulic fluid reservoir (28), adjusts a minimal pressure in the torque converter (1).

23. An apparatus (100) for operating a hydrodynamic torque converter (1) and a converter-bypass clutch (2) of a transmission apparatus, the apparatus comprising: a first line system (20) having a solenoid valve (WDV) and a variable pressure control valve (WKV);a valve stem assembly (WDV_S) of the solenoid valve (WDV) being biased in a first direction by a first spring arrangement (WDV_F) and being biased in a second direction, counter to the first direction, by a controllable pilot pressure (p_VS);a valve stem assembly (WKV_S) of the variable pressure control valve (WKV) being biased in a first direction by a second spring arrangement (WKV_F) and being biased in a second direction, counter to the first direction, by the controllable pilot pressure (p_VS);each of a plurality of control lines (L1, L3, L5, L6, L7, L9) of the first line system (20) is fixed to one of a plurality of control aperture valves (WDV_1, WDV_2, WDV_3, WDV_4, WDV_6, WDV_7, WDV_8) of the solenoid valve (WDV), each of one or more of the plurality of control lines (L1, L3, L5, L6, L7, L9) further communicates with one of a plurality of hydraulic lines (HL3, HL4, HL_6, HL_8, HL9) of a hydraulic line system (22), the solenoid valve (WDV) with the valve stem assembly (WDV_S) of the solenoid valve (WDV) and the first spring arrangement (WDV_F), control flow of a hydraulic fluid from the plurality of control aperture valves (WDV_1, WDV_2, WDV_3, WDV_4, WDV_6, WDV_7, WDV_8) of the solenoid valve (WDV) through the plurality of control lines (L1, L3, L5, L6, L7, L9) and the plurality of hydraulic lines (HL3, HL4, HL_6, HL_8, HL9) to one or more of an inlet side and an outlet side of the torque converter (1) and a piston chamber (27) of the converter-bypass clutch (2);each of another plurality of control lines (L1, L2, L4, L8, L10) of the first line system (20) being fixed to one of plurality of control aperture valves (WKV_1, WKV_2, WKV_3, WKV_4, WKV_5) of the variable pressure control valve (WKV), each of one or more of the another plurality of control lines (L1, L2, L4, L8, L10) further communicating with one of the plurality of hydraulic lines (HL3, HL4, HL_6, HL_8, HL9) of the hydraulic line system (22), the variable pressure control valve (WKV) with the valve stem assembly (WKV_S) of the variable pressure control valve (WKV) and the second spring arrangement (WKV_F) control flow of the hydraulic fluid from the plurality of plurality of control aperture valves (WKV_1, WKV_2, WKV_3, WKV_4, WKV_5) of the variable pressure control valve (WKV) through the another plurality of control lines (L1, L2, L4, L8, L10) and the plurality of hydraulic lines (HL3, HL4, HL_6, HL_8, HL9) to one or more of the inlet side and the outlet side of the torque converter (1) and the piston chamber (27) of the converter-bypass clutch (2);a spent flow of the hydraulic fluid flowing directly from the torque converter (1) to a spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) via the piston chamber (27) of the converter-bypass clutch (2) through the hydraulic line system (22) and the first line system (20); the converter-bypass clutch (2) is pressurized by the spent flow of the hydraulic fluid from the torque converter (1);the converter-bypass clutch (2) being pressurized by a spent flow of hydraulic fluid from the torque converter (1) through the hydraulic line system (22) using an operational control aperture valve (WKV_3) of the pressure control valve (WKV) and an internally thereto connected relief control aperture valve (WDV_2) of the pressure control valve (WDV) having a spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) and byway of the piston chamber (27), which is separated from the spent flow of the torque converter (1), and the spent flow of the torque converter (1) being directly connected with the spent flow control aperture valve (WDV_6) of the solenoid valve (WDV) via the hydraulic line system (22).