The invention relates to a slave cylinder within a hydraulic section for clutch actuation, which slave cylinder is arranged concentrically around a transmission input shaft and has the features of the preamble of claim 1.
A slave cylinder of this type is known, for example, from DE 10 2007 023 A1. In this case an annular piston guided on the inner lateral surface in the housing and subjected to pressure is displaced axially in order to move a bearing race of a disengaging bearing fastened to the end face of said annular piston in the direction either towards or away from the clutch. An objective of this solution is to increase service life by lubrication of the running or guide surfaces. In order to achieve guidance of the piston during its disengagement travel when there is a high proportion of load on the guide surface, the guide length of the annular piston is dimensioned according to the internal diameter of the housing, which forms the guide diameter. It is usual in practice to respect a ratio of 2:1 between the mean housing diameter and the required guide length.
However, in some vehicles, such as hybrid vehicles, in which the transmission input shaft does not have a continuously equal diameter, the space available for installing a slave cylinder is very restricted, so that said slave cylinder must have a compact structure corresponding to the straight region of the transmission input shaft. FR 2 697 879 A1 discloses a slave cylinder which solves this problem in that the piston is formed by two pistons which can be nested concentrically one inside the other, so that the guide length can be lengthened axially in a telescopic manner. To make possible the telescopic retraction and to reduce static friction, a channel with fluid is provided between the sliding surfaces of the two pistons over their length. However, if the fluid film between the sliding surfaces ruptures, this leads to an increase in friction, thereby producing undesired operating noise which leads to a reduction of the service life of the slave cylinder and also to a decrease in driving comfort.
It is therefore the object of the invention to develop a slave cylinder which has a compact structure on account of restricted space conditions and in which the ratio of 2:1 between the mean housing diameter and the required guide length is achieved without the introduction of additional channels for lubricants.
This object is achieved with a slave cylinder having the features of claim 1.
To achieve this object use is made of a slave cylinder with a hollow-cylindrical housing having an axial extent, which housing is open on the clutch side and is delimited at its end on the transmission side by an extension disposed in the radial direction. Axially displaceable within the cylindrical interior of this housing is an annular piston which, like the housing, is arranged concentrically around a transmission input shaft having an axis of rotation. Because the transmission input shaft has in the region of the receptacle of the slave cylinder two different diameters which are directly contiguous to one another, both the inner surface of the housing oriented towards the transmission input shaft and the piston are configured to be congruent in longitudinal section with the external shape of the transmission input shaft, the piston being guided, in the housing, on its internal diameter at its end on the clutch side and on its external diameter at its end on the transmission side.
In this way it is ensured that the guide length meets the requirements and that tilting of the piston over its disengagement travel is avoided, whereby the service life of the slave cylinder can be lengthened.
Advantageous configurations of the invention are apparent from the dependent claims.
The invention is explained in more detail below with reference to an exemplary embodiment and to the associated drawing, in which:
In
In this figure the end of a conduit 17 can be seen, from which it is apparent that the CSC has a hydraulic connection. This conduit 17 is introduced into the housing 3 by means of a plug-in connector 5. In this case the plug-in connector 5 is fixed and also sealed in the receiving bore of the housing 3 by means of an O-ring 5a and a securing element in the form of a wire spring clip 5b. The bore of the inlet, necessary for manufacturing reasons, is closed with the aid of a sealing plug 3a. The housing 3 of the CSC is subdivided radially, parallel to the axis of rotation X of the transmission input shaft 1, by a wall 3b into two functional regions. The first, inner region, which is thus pot-shaped in cross section, serves to receive a piston 7 which is axially movable therein, while the outer functional region serves to fasten the housing 3 to the bearing flange, as is apparent from a fastening screw 4 in the sectional representation below the axis of rotation X. The pot-shaped region therefore has an inner diameter DI and an outer diameter DA. The space formed between these two diameters DA and DI delimits a pressure chamber in the radial direction. In the axial direction this pressure chamber is delimited by the piston 7 and by the inner face of the extension 2c on the clutch side. The drawn-in wall 3b in the housing forms over its axial length a region C, the inner surface of which serves as a guide surface, so that the annular piston 7, which is subjected to pressure by means of an energy accumulator in the form of a preloading spring, is guided with both its internal and its external diameter and therefore is guided on a guide surface in region A and at the same time in region C of the housing. Tilting of the piston 7 during its axial movement is thereby avoided. Region B of the housing 3 serves to receive the energy accumulator 12, the end windings of which bear respectively against the piston 7 and the extension 2c. In order to seal the pressure chamber, the piston 7 has on its internal circumference a sealing element 10 in the form of an inner groove seal, and on its outer circumference a sealing element 11 in the form of an outer groove seal. Connected to the piston 7 on the clutch side is a disengaging bearing 15, the inner race of which is operatively connected to a disk spring 16 (only indicated in the FIGURE). In order to improve the sliding movement, both the internal diameter and the external diameter of the piston 7 are provided with guide bands 8 and 9, via which the piston 7 is in direct contact with the surrounding guide surfaces. The difference of the distance between the two guide bands 8 and 9 yields the guide length L of the piston 7. For adaptation to the stepped transmission input shaft 1 and the stepped bearing flange 2, the annular piston 7 also has a stepped configuration in longitudinal section. It is thereby made possible that the axial distance between the respective outer edges of the guide bands 8 and 9 is increased, and that the piston 7 is therefore guided over the whole guide length L during the disengagement process. Through this design measure whereby the piston 7 is guided, in the housing 3, on its internal diameter at its end on the clutch side and on its external diameter at its end on the transmission side, it is therefore possible to achieve the ratio of 2:1 yielded by the required guide length in relation to the mean guide diameter, the mean guide diameter being formed from the mean value of the sum of the diameters DA and DI. In order to sense the disengagement travel of the piston 7, said piston 7 is provided with an information transmitter in the form of a magnet 14 which is in transmission contact with an information receiver in the form of a sensor 13 mounted on the housing 3.
Number | Date | Country | Kind |
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10 2008 033 699.8 | Jul 2008 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
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PCT/DE09/00896 | 6/29/2009 | WO | 00 | 1/21/2011 |