JPH03533B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a fluid coupling having an input shaft, an output shaft coaxial thereto, a pump impeller and a turbine impeller, and a primary friction coupling half. a friction joint having a body and a secondary friction joint half; a drive shell that houses the turbine impeller and the friction joint and is provided so as not to rotate relative to the pump impeller and the input shaft; and a piston-cylinder. a primary friction coupling having a joint operating device of construction and an axial pressure medium supply passage provided on one shaft, the pressure medium supply passage terminating open at the shaft end proximal to the other shaft; The half body and the cylinder are provided so as not to rotate inward relative to the drive shell body, the output shaft is coupled to the turbine impeller and the secondary friction joint half body so as not to rotate relative to each other, and the friction joint is provided so as not to rotate relative to the drive shell body. The present invention relates to a coupling device for a vehicle drive, which can be operated in one direction by a coupling operating device and in the other direction by a mechanical coupling spring.

Prior Art In a known coupling device of this type (German Patent No. 1 625 722), a secondary friction coupling half of a fluid-operated friction coupling under the action of centrifugal force connects a pressure medium supply channel. The annular plate holds the friction ring and forms the end wall of the annular liquid chamber, with the liquid discharged to the outer edge of the liquid chamber. equipment is provided. A separate supply channel is used for filling the fluid coupling. Friction joints bridging fluid joints are suitable for ship drives and avoid costly axially movable parts of the structure, but known coupling devices for constructing such friction joints require secondary friction joints. The plates forming the halves are axially elastically constructed, are fixed axially to the output shaft and are preloaded by a tension spring beyond their unstressed state in their disconnection position.

From German Patent Application No. 1755971, an auxiliary and parking brake is known which is connected to the transmission of a vehicle, although it is not related to the subject matter of the present invention, and in which the transmission shaft, which is always connected to the driven wheels, is known. , which can be fixed by means of a frictional connection to the non-rotating housing part. This auxiliary/parking brake is engaged by a mechanical spring and released by a piston-cylinder brake operating device. A hydraulic conduit leading from a pump driven by the engine is connected to the cylinder to release the frictional connection when the engine is activated. When the engine is stopped, the device is operated as a parking brake as the hydraulic pressure is no longer present and the spring automatically tightens the brake.

German Patent Application No. 3,203,653 discloses a switching device for a transmission, which is not related to the subject matter of the invention, and which is connected to the drive engine of a motor vehicle via a hydraulic coupling. The manual switching lever of the switching device can be operated according to the H-shaped transmission diagram as usual, but has an additional parking position in the switching path as well as a reverse gear. Once in the park position, the parking gear of the transmission is operated to a position that locks the transmission.

OBJECTS OF THE INVENTION The problem on which the present invention is based is to provide a special parking position of the manual shift lever and the transmission switching means necessary for such a position in a motor vehicle with a manual transmission connected to the drive engine by a hydraulic coupling. It is possible to avoid this by pulling or pushing to start the drive engine, and by shifting gears when the engine is stopped, as in automobiles with transmissions connected to the drive engine by mechanical friction couplings. The purpose is to make it possible to obtain a parking brake effect.

Means for Achieving the Object According to the present invention, a turbine impeller and a drive shell are connected to an end face flange of a crankshaft forming an input side shaft and having a pressure medium supply passage, and a pump impeller. A pressure medium supply passage provided between the cylinder and the cylinder, in which the friction joint is engaged by a joint spring, and which is connected to the cylinder via an outlet at the shaft end, receives an operating pressure that disconnects the friction joint when starting the internal combustion engine. Can be done.

Details and advantages of the invention will emerge from the following description of two embodiments shown in the drawings.

Embodiment In the drawing, a joint axis is shown at 15-15, the cross-sectional portion including this axis and above this axis includes the first embodiment, and the cross-sectional portion below this axis includes the second embodiment. Contains.

Both embodiments are consistent in the following features.

A crankshaft 1 of an internal combustion engine (not shown) used as a drive engine for an automobile has an end face flange 17 at a rear shaft end 14, and a disc-shaped flywheel 19 and a starter annular gear 20 are attached to mounting screws 21 and 2.
2 to the end face flange 17 so as not to rotate relative to each other.

The mounting screw 22 further holds the drive shell 9 by a mounting ring 23 so as not to rotate relative to the end flange 17 of the crankshaft 1. The drive shell 9 is connected at its outer edge by a welded joint 25 so as not to rotate relative to each other. A turbine impeller 4, which together with the pump impeller 3 forms an internal fluid operating circuit, is provided within the drive shell 9 and is connected to the output shaft 2 by a boss device 26 so as not to rotate relative to it.

On the inner edge of the drive shell 9, the two cylinder halves 27 and 28 of the cylinder 12 of the joint actuating device 10 are fixedly secured by mounting screws 9. The cylinder half 27 has a central support bushing 30 which fits into an end support opening 31 in the shaft end 14 of the crankshaft 1.

The piston 11 operating within the cylinder 12 has a central journal 32 on one end face thereof, which journal 32 is centered in a support bush 30 for axial movement. This journal 32, which is configured as a hollow journal, supports the output shaft 2 via an inner rolling bearing 33, the rear shaft end 35 of which is supported via a rolling bearing 36 in a boss 37, which 37 is fixed to the outer shell 24 by a mounting screw 38 so as not to rotate relative to the outer shell 24. The rear shaft end 35 has an end flange 39 for connecting a manual transmission by means of a conventional separation joint or main joint.

1 used to apply pressure to the piston 11
The second pressure chamber 40 is connected to the support opening 31 via an axial groove 41 around the journal 32;
The pressure medium supply channel 13 with the outlet 18 in this support opening 31 is connected to the joint axis 1 in the crankshaft 1.
5-15 and is connected to the internal combustion engine's lubricating system.

The boss device 26 has corresponding flanges and fixes them to each other in order to support a plurality of coiled joint springs 16 having spring axes parallel to the joint axis 15-15 and uniformly distributed in the circumferential direction. A support ring 42 that is fixedly connected to the support sleeve 43 by a connecting stud 46
It has This support sleeve 43 is held immovably on the output shaft 2, in particular by spline teeth 47. The other end of the joint spring 16 acts on a pressure ring 45 which is common to both embodiments and is concentric with the joint axis 15-15. The rings 42 and 45 are provided so that they can move relative to each other in the axial direction, and are prevented from rotating relative to each other by engaging teeth 49.

Both embodiments differ in the following features.

In the example of the upper cross-sectional part, the turbine impeller 4
A pressing ring 45 is constructed integrally with an impeller boss 44 which is fixedly welded to the outer shell 48 of the rotor at its radially inner side.

A conical ring forming the secondary friction joint half 7 of the friction joint 8 is welded radially outwardly to the outer shell 48 to form a primary friction joint half which is held immovably on the inner wall of the drive shell 9. It cooperates with a conical ring as body 6.

In the embodiment of the lower cross-section, the impeller boss part 50, which is constructed in one piece with the support ring 42, is fixedly welded to the outer shell 48 on the radially inner side. The pressing ring 45 is constructed integrally with a conical ring forming the secondary friction joint half 7 of the friction joint 8, and the conical ring cooperating with this conical ring to form the primary friction joint half 6 is connected to the cylinder half. An integral protrusion protruding in the axial direction of the outer edge of 28 is formed.

In both embodiments, the piston 11 has a centrally actuating sleeve 53 on its end face close to the joint spring, which sleeve 53 passes through a bore in the cylinder half 28 and forms an annular shape concentric to the joint axis 15-15. By acting on the pressure plate 52, the friction joints 8 of both embodiments are separated in the same way. This pressing plate 5
2 can act on the pressing ring 45 through the compression needle bearing 51 by its outer edge, thereby compressing the joint spring 16.

The operation of the coupling devices 5, 8 is as follows.

When the internal combustion engine is rotating, the pressure medium supply channel 13 is subjected to operating lubricating pressure, which pressure acts on the appropriately designed effective pressure surface of the piston 11 and causes the piston 11-pressure plate 552 . Press ring 45
axially by the opening clearance of the friction joint 8. As a result, slippage occurs within the fluid coupling 5, thus making it possible to damp rotational vibrations and transmit torque.

When the internal combustion engine stops, the pressure medium supply passage 13
The pressure in the press ring 4 becomes almost atmospheric pressure, so that the pressure in the press ring 4
5-Moving the press plate 52-piston 11 system in the axial direction in the engagement direction, the opening clearance becomes zero and the friction torque of the internal combustion engine, in which the frictional connection of the friction joint 8 is stopped, is transmitted to the transmission. The total force of the joint spring 16 is sufficient to ensure that

A particular advantage of the coupling device according to the invention is that the friction coupling only needs to transmit the drag torque of the engine.

[Brief explanation of the drawing]

The figure is a sectional view along the axis of the coupling device according to the invention. 1...Input side shaft, 2...Output side shaft, 3...Pump impeller, 4...Turbine impeller, 5...Fluid coupling, 6...Primary friction joint half, 7...Secondary friction Joint half body, 8...Friction joint, 9...Drive shell, 1
0...Joint operation device, 11...Piston, 12...
...Cylinder, 13...Pressure medium supply passage, 14...
...Shaft end, 16...Joint spring, 17...End flange, 18...Outlet.

Claims (1)

[Claims] 1. A fluid coupling having an input shaft, an output shaft coaxial with the input shaft, a pump impeller and a turbine impeller, a friction joint having a primary friction joint half and a secondary friction joint half, and a turbine. A drive shell housing an impeller and a friction coupling and provided so as not to rotate relative to the pump impeller and input shaft, a piston-cylinder structure coupling operating device, and an axis provided on one shaft. directional pressure medium supply passage, which pressure medium supply passage terminates open at the shaft end proximal to the other shaft, so that the primary friction coupling halves and the cylinder rotate inwardly relative to the drive shell. The output shaft is connected to the turbine impeller and the secondary friction joint half so as not to rotate relative to each other, and the friction joint is connected in one direction of the joint axis by a joint operating device and in the other direction by a mechanical joint. In those operable by means of a spring, the turbine impeller 4 and the drive shell 9 are located between the end flange 17 of the crankshaft 1 forming the input shaft and having the pressure medium supply passage 13 and the pump impeller 3. A pressure medium supply channel 13 is provided, in which the friction coupling 8 is engaged by a coupling spring 16 and which is connected to the cylinder 12 via an outlet 18 in the shaft end 14, for actuation of disconnecting the friction coupling 8 during starting of the internal combustion engine. A coupling device for a vehicle drive device, characterized in that it can receive pressure.