Device for the operation of a starter mechanism that can be brought into active connection with a hydraulic supply circuit of a transmission unit

Abstract

A device for operating a starter mechanism actively connected with a hydraulic supply circuit of a transmission unit. The starter mechanism has a piston chamber subject to hydraulic pressure for activating a frictional shift element and a hydraulic chamber subject to hydraulic pressure for the cooling and lubricating an area of the starter mechanism. A hydraulic pressure between a lubrication pressure control port of a second pressure relief valve and the hydraulic chamber and equivalent to a lubrication pressure, is exerted on a second back pressure outlet port of a first relief valve, which acts on a valve slide of the first relief valve in the opposite direction relative to the working pressure exerted on a first back pressure outlet port of the first relief valve so that the pressure feed-back of the hydraulic pressure to the first relief valve occurs additively to the pilot signal characteristic of the first relief valve.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be described, by way of example, with reference to the accompanying drawings. For the sake of clarity, the same reference numerals are used for components with the same structure and function. The drawings show:

FIG. 1A is a schematic circuit diagram of the device according to the invention for operating a starter mechanism made as a wet-running disk clutch;

FIG. 1B is two respective variations of the working pressure in an inlet area of the piston chamber of the starter mechanism and of the lubrication pressure in the inlet area of the hydraulic chamber of the starter mechanism, produced by pilot pressures with which a first pressure relief valve and a second pressure relief valve are controlled;

FIG. 2 is a graphical comparison of the volume/pressure characteristic of the starter mechanism of FIG. 1A in the inlet area of the hydraulic chamber, directly in the hydraulic chamber, and in the return area of the hydraulic chamber;

FIG. 3 is the first pressure relief valve of the device represented in FIG. 1A, in a very schematic, enlarged longitudinal section view, shown in isolation;

FIG. 4A is a representation corresponding to that of FIG. 1A, showing another example embodiment of the device according to the invention

FIG. 4B are variations of the working pressure, shown in FIG. 4A, in the inlet area of the piston chamber and of the lubrication pressure in the inlet area of the hydraulic chamber, produced by pilot pressure control of the first and second pressure relief valves, represented as in FIG. 1B;

FIG. 5A is a hydraulic layout of a further example embodiment of the device according to the invention, which is made with an additional pilot valve;

FIG. 5B are variations of the working pressure in the inlet area of the piston chamber and variations of the hydraulic pressure in the inlet area of the hydraulic chamber downstream from the pilot valve of the device shown in FIG. 5A;

FIG. 6A is a hydraulic layout of another example embodiment of the device according to the invention;

FIG. 6B are variations of the working pressure in the inlet area of the piston chamber of the starter mechanism and variations of the hydraulic pressure in the inlet area of the hydraulic chamber downstream from the pilot valve of the device in FIG. 6A;

FIG. 7A is a hydraulic layout of a further example embodiment of the device according to the invention, in which the pilot valve can additionally be controlled by a pilot pressure set by a magnetic valve

FIG. 7B are variations of the working pressure in the inlet area of the piston chamber of the starter mechanism of the device shown in FIG. 7A, and variations of the hydraulic pressure in the inlet area of the hydraulic chamber downstream from the pilot valve;

FIG. 8A is a hydraulic layout of another example embodiment of a device according to the invention;

FIG. 8B are variations of the working pressure in the inlet area of the piston chamber, and of the hydraulic pressure in the inlet area of the hydraulic chamber of the starter mechanism in FIG. 8A;

FIG. 9A is a hydraulic layout of a further example embodiment of a device according to the invention for the operation of a three-line converter;

FIG. 9B are variations of the working pressure in the inlet area of the piston chamber of the converter bridging clutch of the three-line converter, and of the hydraulic pressure in the inlet area of the hydraulic chamber of the hydrodynamic torque converter of the three-line converter downstream from the pilot valve, produced by pilot pressures of the first and second pressure relief valves and the pilot valve of the device shown in FIG. 9A;

FIG. 10A is a hydraulic scheme of another example embodiment of the device according to the invention for the operation of a starter mechanism made as a two-line converter, and

FIG. 10B are variations of the working pressure in the inlet area of the piston chamber of a converter bridging clutch of the two-line converter shown in FIG. 10a, and variations of the hydraulic pressure in the inlet area of the hydrodynamic torque converter downstream from the pilot valve, produced by pilot pressures of the first and second pressure relief valves and the pilot valve.

Claims

1-27. (canceled)

28. A system (1) controlling a starter mechanism (3) which is actively connected with a hydraulic supply circuit (2) of a transmission unit, the system comprising: the starter mechanism having a converter bridging clutch (27), a piston chamber (4) and a hydraulic chamber (6), the converter bridging clutch (27) being actuated, upon introduction of a working pressure (p_A) into the piston chamber (4), and an area of the starter mechanism (3) being cooled and lubricated upon introduction of a lubrication pressure (p_SD) to the a hydraulic chamber (6);a first pressure relief valve (DBV1) regulating the working pressure (p_A) delivered to the piston chamber (4);a second pressure relief valve (DBV2) regulating the lubrication pressure (p_SD) delivered to the hydraulic chamber (6);a first pilot pressure (p_VS(DBV1)) controlling a valve slide (DBV1_S) of the first pressure relief valve (DBV1), and a first pressure control valve (10) and a first spring device (DBV1_F) controlling the first pilot pressure (p_VS(DBV1));a second pilot pressure (p_VS(DBV2)) controlling a valve slide (DBV2_S) of the second pressure relief valve (DBV2), and a second pressure control valve (11) and a second spring device (DBV2_F) controlling the second pilot pressure (p_VS(DBV2));the working pressure (p_A) exerting force on a first back pressure outlet port (DBV16) of the first pressure relief valve (DBV1) and the lubrication pressure (p_SD) exerting force on a back pressure outlet port (DBV21) of the second pressure relief valve (DBV2);a hydraulic pressure (p_vor, p_in, p_na), in an area between a lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2) and a return area of the hydraulic chamber (6), exerting a force on a second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1), and the hydraulic pressure (p_vor, p_in, p_na) being equivalent to the lubrication pressure (p_SD); andthe hydraulic pressure (p_vor, p_in, p_na) exerting a force on the valve slide (DBV1_S) of the first pressure relief valve (DBV1) in an opposing direction to the force of the working pressure (p_A) exerted on the first back pressure outlet port (DBV16) of the first pressure relief valve (DBV1), such that a feed-back of the hydraulic pressure (p_vor, p_in, p_na) exerted on the first pressure relief valve (DBV1) is added to a pilot signal characteristic of the first pressure relief valve (DBV1).

29. The system according to claim 28, wherein a first active surface area (14) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1), influenced in an area of the second back pressure outlet port (DBV12) by the hydraulic pressure (p_in), is essentially equivalent to a second active surface area (15) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1), and the second active surface area (15) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1) is influenced by the working pressure (p_A) via the first back pressure outlet port (DBV16) of the first pressure relief valve (DBV1) during return flow of the hydraulic pressure (p_in) from a return area of the hydraulic chamber (6) to the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1).

30. The system according to claim 28, wherein a first active surface area (14) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1), influenced in an area of the first back pressure outlet port (DBV16) by the hydraulic pressure (p_vor), is smaller than a second active surface area (15) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1) influenced by the working pressure (p_A) via the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1), during return flow of the hydraulic pressure (p_vor) from an inlet area hydraulic chamber (6) to between the second pressure relief valve (DBV2) and the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1).

31. The system according to claim 28, wherein a first active surface area (14) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1), influenced in an area of the first back pressure outlet port (DBV16) by the hydraulic pressure (p_na), is larger than a second active surface area (15) of the valve slide (DBV1_S) of the first pressure relief valve (DBV1) influenced by the working pressure (p_A) via the first back pressure outlet port (DBV16) of the first pressure relief valve (DBV1) during return flow of the hydraulic pressure (p_na) from the hydraulic chamber (6) to a return area of the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1).

32. The system according to claim 28, wherein the working pressure (p_A) exerted on the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1) opposes the first pilot pressure (p_VS(DBV1)) which is controlled by the first pressure control valve (10) and which controls the first pressure relief valve (DBV1).

33. The system according to claim 28, wherein the first pressure relief valve (DBV1) has a third back pressure outlet port (DBV13) communicating with a third pressure relief valve (DBV3) and a working pressure control port (DBV14) of the first pressure relief valve (DBV1) by way of the valve slide (DBV1_S) of the first pressure relief valve (DBV1), and the working pressure control port (DBV14) of the first pressure relief valve (DBV1) influences the piston chamber (4) with the working pressure (p_A) and actively communicates with the first back pressure outlet port (DBV16) of the first pressure relief valve (DBV1).

34. The system according to claim 33, wherein the first pressure relief valve (DBV1) has a supply control port (DBV15) communicating with a primary pressure circuit of the transmission unit, and the supply control port (DBV15) of the first pressure relief valve (DBV1) communicates with the working pressure control port (DBV14) of the first pressure relief valve (DBV1) when communication between the working pressure control port (DBV14) and a third pressure relief control port (DBV13) of the first pressure relief valve (DBV1) is blocked by the valve slide (DBV1_S).

35. The system according to claim 28, wherein the second pressure relief valve (DBV2) comprises a supply control port (DBV22) which communicates with a secondary pressure circuit of the transmission unit, the supply control port (DBV22) further communicates with the lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2) by way of the valve slide (DBV2_S), the hydraulic chamber (6) of the starter mechanism (3) is influenced by the lubrication pressure (p_SD) via the lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2) which communicates with both the back pressure outlet port (DBV21) of the second pressure relief valve (DBV2) and to the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1).

36. The system according to claim 35, wherein the lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2) communicates with a pressure relief control port (DBV24) of the second pressure relief valve (DBV2) when communication between the lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2) and the supply control port (DBV22) of the second pressure relief valve (DBV2) is blocked by the valve slide of the second pressure relief valve (DBV2).

37. The system according to claim 34, further comprising a pressure regulation valve (DRV) located between a primary pressure circuit and the first and the second pressure control valves (10, 11), a primary pressure (p_prim) of the primary pressure circuit is regulated to a reducing pressure (p_red) by the pressure regulation valve (DRV).

38. The system according to claim 28, wherein the hydraulic chamber (6) is influenced by the lubrication pressure (p_SD) via a pilot valve (SV) located between the second pressure relief valve (DBV2) and the hydraulic chamber (6).

39. The system according to claim 38, wherein the lubrication pressure (p_SD) influences the supply circuit (2) of the transmission unit via the pilot valve (SV).

40. The system according to claim 38, wherein a return of the hydraulic chamber (6) communicates with a back pressure outlet port (SV5) of the pilot valve (SV) which actively communicates, by way of a valve slide (SV_S) of the pilot valve (SV), with a first outlet control port (SV4) of the pilot valve (SV) which communicates with the supply circuit (2).

41. The system according to claim 38, wherein the pilot valve (SV) comprises a lubrication pressure control port (SV3) which communicates with the lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2), such that the lubrication pressure control port (SV3) of the pilot valve (SV) communicates, via a valve slide (SV_S) of the pilot valve (SV), with an inlet control port (SV2) of the pilot valve (SV), and the inlet control port (SV2) of the pilot valve (SV) communicates with an inlet of the hydraulic chamber (6).

42. The system according to claim 41, wherein the lubrication pressure control port (SV3) of the pilot valve (SV) communicates with the outlet control port (SV4) of the pilot valve (SV), via the valve slide (SV_S) of the pilot valve (SV), when the communication between the lubrication pressure control port (SV3) of the pilot valve (SV) and the inlet control port (SV2) of the pilot valve (SV) is blocked by the valve slide (SV_S) of the pilot valve (SV).

43. The system according to claim 41, wherein the inlet control port (SV2) of the pilot valve (SV) communicates with the second back pressure outlet port (DBV12) of the first pressure relief valve (DBV1).

44. The system according to claim 40, wherein the pilot valve (SV) has a first pressure relief control port (SV6) which communicates with the back pressure outlet port (SV5) of the pilot valve (SV).

45. The system according to claim 44, wherein the first pressure relief control port (SV6) of the pilot valve (SV) communicates with a fourth pressure relief valve (DBV4).

46. The system according to claim 45, wherein the pilot valve (SV) has a second pressure relief control port (SV9) which communicates with an inlet control port (SV2) which is connected with the fourth pressure relief valve (DBV4).

47. The system according to claim 43, wherein a control line (L5), having a throttle device (D1), is located between: the lubrication pressure control port (DBV23) of the second pressure relief valve (DBV2) and the lubrication pressure control port (SV3) of the pilot valve (SV), andthe inlet control port (SV2) of the pilot valve (SV) and the second return control port (DBV12) of the first pressure relief valve (DBV1).

48. The system according to claim 40, wherein the pilot valve (SV) has a second outlet control port (SV8) which communicates with a lubrication pressure control port (SV3) of the pilot valve (SV).

49. The system according to claim 38, wherein a fifth pressure relief valve (DBV5) is located between the pilot valve (SV) and the supply circuit (2) of the transmission unit.

50. The system according to claim 38, wherein both the first pressure relief valve (DBV1) and the pilot valve (SV) are influenced by the first pilot pressure (p_VS(DBV1), p_VS(SV)) from the first pressure control valve (10).

51. The system according to claim 50, wherein the pilot valve (SV) and the first pressure control valve (10), associated with the first pressure relief valve (DBV1), are alternatively influenced by the first pilot pressure (p_VS(SV)) via an OR-valve (21).

52. The system according to claim 28, wherein the second pressure control valve (11), which corresponds with the second pressure relief valve (DBV2), adjusts the second pilot pressure (p_VS(DBV2)) which passes, via the first pressure relief valve (DBV1), to the second pressure relief valve (DBV2).

53. The system according to claim 28, wherein the starter mechanism (3) is a wet-operating frictional disk clutch.

54. The system according to claim 28, wherein the starter mechanism (3) is a hydrodynamic torque converter and the converter bridging clutch (27) is one of a two-line converter and a three-line converter.