KR100419704B1 - Hydraulic separator for friction clutches - Google Patents

Abstract

The present invention relates to a hydraulic type restraining and releasing device for a friction clutch in an automobile having a single case, in which a guide pipe is inserted in a radially spaced relation to the inner wall at a central groove of the case, A piston formed as a telescope piston is guided so as to be movable in the axial direction while bridging the radial gap between the guide pipe and the inner wall. According to the present invention, a restraint / release device 1b is provided to obtain a structure for reducing the necessary drying space, and this restraint / release device has a secondary piston 9b formed in the shape of a covering, Coaxially surrounds the primary piston 8b which is movably guided on the guide jacket 6b.

Description

Hydraulic separator for friction clutches

A separating device of this kind is known from JP 3-186 620-A. The structure of this separating device comprises a telescopic piston, which consists of two individual pistons, which are coaxially intermeshed and movable with respect to one another at their end positions. The pistons, which in each case are formed in the form of a hollow cylinder, have a relatively large wall thickness, which adversely affects the required radial structural space of the device. At the pressure side, each piston also has a radially outwardly directed attachment, in which an annular groove is formed for receiving the sealing portion. In this case, the radially inner piston abuts the inner wall of the outer piston, and the outer piston abuts the wall of the housing. Another sealing portion is provided for sealing the annular gap between the guide sleeve of the case and the inner wall of the inner piston. The known separating device thus has a large component range besides the disadvantages of the drying space as well as the result of cost disadvantages.

The present invention relates to a hydraulic separator for a friction clutch according to the features of the preamble of claims 1 and 26.

Further details of the invention can be seen in the following description of four embodiments, which are all in the form of eighteen drawings:

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded perspective view of a telescopic piston according to the present invention shown in a pressure-filled state therein;

Fig. 2 is an exploded perspective view of an intake cylinder housing corresponding to Fig. 1 with a different first piston sealing portion; Fig.

Figure 3 shows a half-sectioned separating device, arranged in a first piston, having a circumferential outer ring and a clutch release bearing at the engaged end position:

Figure 4 shows the separating device according to Figure 3 in an isolated position (end position);

Fig. 5 shows a separating device with an axial space-optimized intake cylinder housing shown therein at an end position where the clutch release bearing engages;

Fig. 6 shows the separation device shown in Fig. 5 at the discrete position (end position); Fig.

7 shows a half-sectioned separating device, with its clutch release bearing having an inner ring to rotate;

Fig. 8 shows the separating device according to Fig. 7 at the disengaged position (end position) of the clutch separating bearing;

Figure 9 shows a separating device, which can be used through the reinforcement, and in which a groove sealing ring is provided for sealing the pressure chamber, in which the groove sealing ring and the groove sealing ring are snap-

Figure 10 shows the structure of a separating device according to the invention in which a pressure spring is inserted between the housing and the carrier disc associated with the clutch separating bearing to eliminate the preliminary pressure valve;

11 is a view showing the stroke limitation of the second piston of the separating device according to the present invention;

12 is a perspective view illustrating a second piston which is fixedly inserted between a guide sleeve and a housing;

13 is an elastic ring inserted in the housing, which is located in the peripheral groove of the second piston to reach the position fixation of the second piston;

14 shows a second ring injected into the housing in a suitable manner;

15 is a view of a separating device having a conduit-and a spouting connection coming out of the housing in a radial direction;

FIG. 16 is a cross-sectional view of the separation apparatus according to FIG. 15 taken along the line B-B; FIG.

17 is a longitudinal sectional view of the separating apparatus, showing a modification to the separating apparatus shown in Fig. 7; Fig.

Fig. 18 is a sectional view taken along line A-A in Fig. 17; Fig.

It is therefore an object of the present invention to provide a hydraulic separator which can be advantageously manufactured at a cost and has the advantages of assembly and which maximizes the efficiency of the weight as well as the drying space.

This problem is solved by the features mentioned in the characterizing part of claims 1 and 26.

The hydraulic separator constructed in accordance with the present invention has a second piston formed in the shape of a lid for the formation of a telescopic piston which coaxially surrounds the first piston in contact therewith. The first piston is guided over its inner diameter in the guide sleeve and the second piston is guided over its outer surface in the housing of the separating device. This piston arrangement allows for the short, axial configuration required, in an advantageous manner. The housing in which the conventional structures with a one-piece piston in addition to the guide sleeves ensuring guidance throughout almost the entire stroke of operation has a reduced axial length of structure as a result of which the weight and cost advantages . The piston according to the invention further improves handling due to the reduced length of the structure, through which the assembly can be simplified.

According to claim 1, a sealing portion is provided for sealing the second piston in the housing, which is provided in the annular groove, which contacts the outer surface of the second piston under a pre-stressed condition. A sealing ring, in particular a groove sealing ring, is provided on the front side of the sealing ring for the sealing of the first piston, the sealing lips of the groove sealing ring arranged on both edge regions of the sealing ring, on the one hand, On the one hand, and on the inner wall of the second piston on the other hand.

A groove sealing ring arranged inseparably in contact with the reinforcing portion is suitably used for the purpose according to claim 2, wherein the reinforcing portion is snap-engaged with the annular piston again in conformity with the shape. For this purpose, vulcanization is proposed as an advantageous way of integrating both components into one unit. Alternatively, the present invention contemplates a grooved sealing ring, in which case the reinforced portion is partially surrounded by a sealing material, and the reinforcing section exiting the grooved sealing ring is secured to the annular piston.

The present invention ensures that the first piston has a smaller travel resistance than the second piston according to claim 3. This method of operation is obtained due to the smaller sealing diameter of the groove sealing ring, which is provided for the first piston, as compared to the sealing portion provided in the housing for sealing the second piston. In addition, the relatively weak sealing lips of the home sealing ring cause less friction than the sealing rings that are guided in the housing, while touching the housing surface under stress beforehand for the sealing of the second piston. According to the different displacement resistance, in the case of the operation of the separating device according to the invention caused through the operation of the clutch pedal, first the movement of the first piston is made before the second piston is moved.

According to claim 4, it is an object to manufacture a guide pipe and a second piston without cutting through deep drawing. The idea of the present invention is also to use the drawable parts which are advantageously manufacturable in terms of cost, for example, after gas nitriding and after honing, blanching and polishing and subsequent salt bath-oxidation treatment as corrosion protection However, through this, it is possible to eliminate the conventional, costly surface layer formation so far in the guide hole of the housing.

According to a fifth aspect of the present invention, in the structure of the separating device according to the present invention, it is preferable that the stopper is formed in the housing through the collar which the second piston points radially outward with one side. In order to make the stroke limit of the first piston, according to claim 6, a second piston is provided with a collar pointing radially inwardly, the collar covering and gripping the attachment part with the first piston, It forms the administrative limit.

The dense structure is emphasized in accordance with claim 7, wherein a generally rotationally symmetrical groove is provided in the housing and the clutch release bearing can be accommodated in the case of a position where the friction clutch is engaged.

The construction of the invention according to claims 8 and 9 relates to the formation of the inner ring and the outer ring of the clutch separating bearing. According to claim 8, the separating device according to the present invention comprises an inner ring fixed to the first piston and fixed to the first piston, and a rotatably arranged outer ring of the friction clutch. The arrangement according to claim 9, on the contrary, comprises an outer ring which is rotationally fixedly and indirectly coupled with the first piston, and also a rotating inner ring.

According to claim 10, a detachable bearing fixation is provided which is adapted to the shape between the first piston and the bearing of the clutch release bearing, in order to make a detachable fixation of the clutch release bearing. This arrangement allows replacement of damaged parts of the hydraulic separator, if necessary, without the housing and clutch separating bearing having to be exchanged together in case of damage.

According to claim 11, there is provided a carrier disc between a fixedly arranged outer ring and a first piston of a clutch separating bearing, wherein the carrier disc has a snap fit to the shape, in order to achieve a simple, cost- And is fixed to the first piston through engagement.

In order to effectuate an effective sealing between the inner ring and the outer ring of the clutch separating bearing, a supporting disk reinforced according to claim 12 is provided, which is supported by the force of the serpentine spring, Touch. The support discs according to the invention effectively prevent adverse lubricant emissions from the clutch release bearings and additionally allow radial adjustment as well as axial and axial ringing of the outer ring. These measures favor the service life of the clutch separating bearing.

According to claim 13, it is the object of the invention to provide an attenuation ring between the outer ring and the carrier disc, which blocks the radial movement which is attenuated, i.e. avoiding large radial deviations of the outer ring. According to the invention, for this purpose, an attenuation ring is provided, which is fixed to the outer ring collar of the outer ring on the inner side, which is connected to the concentric section of the guide sleeve via elastically- Touch. A plurality of resilient spring arms, preferably bridging the radial gap in the damping ring made of plastic, are located distributed around the spring arms, which allow for a limited radial deviation of the outer ring from the clutch release bearing .

In one advantageous configuration of the damping ring, claim 14 provides an axial sealing lip on the side of the front side of the damping ring that points to the clutch release bearing. This axial sealing lip is integrally formed in the damping ring as a radially inwardly directed shoulder for this purpose and seals in contact with the vertical section of the carrier disc under a pre-stressed condition at its radially inner end. In this valve section, the following areas are formed corresponding to the inner ring contour, which are complementary to the corresponding inner ring section and form a maze-shaped sealing part to avoid lubricant loss.

In a further advantageous embodiment of the invention according to claim 15, the inner ring and the outer ring also have a section towards the housing, which are spaced apart radially with respect to one another, whereby the resulting drying space And may be formed as a lubricant reservoir for lubricating the roller body of the clutch separating bearing. According to claim 16, a reservoir body filled with lubricant can be inserted into the drying space, wherein the reservoir body can be arranged in a fixed or rotating inner ring or outer ring of the clutch release bearing for lubricant supply of the roller body. According to claim 17, carrier grooves are formed for targeted delivery of the lubricant material, which are in each case arranged in the facing inner or outer ring of the lubricant reservoir or reservoir body.

The inventive idea according to claim 18 is characterized in that, in the case of an engaged friction clutch, the forming ring, which fills an annular gap which is adjusted between the clutch separating bearing and the housing and which protrudes into the corresponding groove of the housing in the case of a separate friction clutch . This advantageous configuration effectively prevents dust from entering the rotationally symmetrical grooves in the guide passage between the housing and the clutch separating bearing and between the first and second pistons.

According to claim 19, it may be advantageous for the second piston to be attached to a supporting means for causing a distance control restriction or a position fixation of the second piston. This arrangement enables, for example, the multiple use of the second piston, thereby contributing to cost reduction and restriction of part variability. According to the present invention, in this case, the fit of the maximum piston stroke through limitation or fixation of the second piston is considered. According to the invention of claim 20, it is proposed that an elastic ring is provided in the annular groove in the housing, the elastic ring being located in the circumferential groove of the second piston in its installed state, The width of the ring is exceeded and thereby the stroke limit of the second piston is adjusted. Alternatively, according to claim 21, the resilient ring is installed into the peripheral groove of the second piston, which is located in the mounting position in the annular ring of the housing, wherein the width of the annular groove exceeds the width of the resilient ring.

In order to realize a simple position fixation of the second piston, the invention proposes an elastic ring which is located in the housing according to claim 22, which is located in the peripheral groove of the second piston, which is suitable for the width of the elastic ring.

An alternative position fixation of the second piston is provided according to claim 23 for which the second piston has its one end in its installed position and is supported on the annular flange of the guide sleeve and has its other end radially inward And contacts a housing band via a band formed toward the housing band. In order to create a sufficient leakage cross section in the region of the annular flange, the annular flange is formed with protrusions projecting axially in the contact area of the second piston, and the second piston is supported on these protrusions.

Claim 24 is the casting of the second piston directly from the housing material as an insert part in the pressure casting or plastic injection molding process for the manufacture of the housing through which the positioning of the second piston is achieved at the same time. Through this manufacturing process, the machining of the holes for receiving the second piston is avoided in an advantageous way. For optimization of position fixation, the shell surface of the second piston according to claim 25 has at least one circumferential groove, which is filled by the casting material in the process of manufacturing the housing.

The invention according to claim 26 provides an arrangement of pressure springs for the maintenance of a preload between a clutch release bearing and a clutch adjustment spring. The structure according to the invention comprises a piston consisting of a first piston and a second piston, which are coaxially arranged so as to be movable longitudinally relative to each other, and which form a telescopic piston. According to this structural configuration, the clutch release bearing is fixed to the first piston and the pressure spring is installed between the housing and the bearing ring of the clutch release bearing. Such a structure according to the present invention does not require a preliminary pressure valve and therefore represents a cost reduction. In addition, with respect to the low failure occurrence of the separator, there is less component parts.

According to an advantageous construction, according to claim 27, a carrier disc belonging to the first piston is proposed, on which a clutch release bearing is supported on one side and a pressure spring is supported on the opposite side. According to Claim 28, an axially projecting attachment portion is provided on the carrier disk, and the spring end of the pressure spring abuts against the attachment portion in a state in which stress is applied in advance. It is also contemplated by the present invention that the attachment portion centering the spring ends inside or outside.

In order to make the advantageous short construction length of the pressure spring, a conical spring is installed according to claim 29, which provides additional safety against unfavorable bending, and therefore does not require any kind of guidance.

According to claim 30, it is an object to propose a housing for a separating device, wherein the housing is provided integrally with a connection projecting radially from the clutch housing or in the direction of the outer wall of the clutch housing. Also, the joints, which are represented as welded tubes, can be eliminated at the expense of additional costly assembled pipe conduits; In addition to this, the number of sealing locations to be sealed is reduced, that is, the pipe threading in the direct housing is eliminated and also the required alignment of the pipe conduits so far in assembling can be eliminated, resulting in cost reduction.

In an advantageous configuration of the present invention according to claim 31, the conduit connection includes a separate spout connection or discharge connection through which the initial filling of the hydraulic system during the initial assembly of the hydraulic separator is simplified, Emissions of the system can also be implemented effectively. According to a preferred configuration of the connector, the free end is provided with a discharge connection and a conduit connection, wherein the connections are spaced apart in parallel and arranged at right angles to the connection tube. The connecting parts are guided through the hole of the clutch housing in the installed state of the separating device according to the invention, so that there is a possibility of easy connection.

According to claim 32, the connecting piece is arranged with two supply ports extending parallel to one another, the supply ports being in communication with the conduit connections and the outlets formed in the discharge connection. According to claim 33, in order to achieve an effective sealing of the supply openings, they are sealed by separate closing parts, i.e. spheres, on the end side.

In order to simply carry the sphere into the longitudinal holes, the longitudinal holes according to claim 34 extend conically in the end side. After the end position is achieved, caulking is also provided which is suitable for the shape of the wall region of the longitudinal bore, which ensures a limited radial coverage of the sphere, through which the sphere is suitably supported .

According to claim 35 and claim 37, as an alternative to the parallel arrangement, alternating arrangements of the conduit connections and of the discharge connections are also formed which depend on a pre-determined installation rate, Respectively.

The idea of the present invention comprises the construction of a part of the housing and of the connector according to claim 36. This unit can be made advantageous in terms of cost in this case as a casting, in which aluminum pressure casting is particularly suitable.

1 and 2 show the structure of the separating device 1a according to the present invention in a half-sectional view, respectively, under pressure. The separating device 1a is provided with a housing 2a which is fixed to the gearbox housing, not shown in Figs. 1 and 2, in a state of being installed, via the front side 3. Fig. In the housing 2a, a plurality of step-shaped grooves 4 formed rotationally symmetrically at the center are made. A guide sleeve 6a centered on the annular flange 5 at the front side 3 extends in the groove 4 while maintaining a radial gap with respect to the groove 4 of the housing 2a . 1 and 2 do not show a pressure axis extending in the guide sleeve 6a, which connects the friction clutch to the transmission gear box. A first piston 8a is guided on the outer surface 7 of the guide sleeve 6a where the first piston 8a contacts the guide sleeve 6a in a radial direction through closely spaced intervals. The first piston (8a) is provided with a groove (24) for accommodating lubricant in the hole wall. The first piston 8a having a circular ring-shaped cylinder shape is axially movable on the guide sleeve 6a. A second piston 9a coaxially surrounding the first piston 8a is also movably inserted in the groove 4 of the housing 2a in the axial direction. In order to adjust the center of the guide sleeve 6a, the overlapping portion 10 formed in the annular flange 5 is used, which is in contact with the first end 11 of the groove 4. The guide sleeve 6a is also used for receiving the support ring 12, and an axial sealing ring not shown in this support ring can be inserted. The support ring 12 has a layered shape and is centered in the guide sleeve 6a. The support ring 12 contacts the annular flange 5 via the vertical section. The first piston 8a has a drive body 23 at its end facing the friction clutch on its shell surface which cooperates with the collar 16 of the second piston 9a.

The pressure chamber 13 surrounded by the housing 2a, the guide sleeve 6a, the first piston 8a and the second piston 9a is connected to the pressure medium supply source via one supply port 14 . The pressure action of the pressure chamber 13 causes the axial movement of the first piston 8a and the second piston 9a where the different movement resistance of the two pistons causes the first piston 8a and the second piston 9a to move, An axial movement of the first piston 8a takes place and the stopper has a rotating collar 16 pointing inward in the radial direction and a mounting collar 16 . The synchronous axial movement of the second piston 9a is then performed until the collar 18 facing radially outward of the second piston abuts the housing 2 forming the stopper 19 together. In the case of the reversal of the piston movement, the first piston 8a is first brought into contact with the collar 16 of the second piston 9a for the installation of the groove sealing ring 20 which is inserted outside in the first piston 8a And then both pistons are moved to their end positions, in this case it leads from the annular flange 5 to the collar 18 for installation. The different moving resistance between the first piston 8a and the second piston 9a is determined through the sealing of the two pistons and these pistons generate different frictional forces, especially on the basis of different sealing diameter.

The first piston 8a has a groove sealing ring 20a on which the sealing lips contact the guide sleeve 6a and on the other hand the second piston 9a. A sealing ring inserted between the second piston 9a and the housing 2a is inserted into the peripheral groove of the housing 2a starting from the pressure chamber 13 and is in contact with the second piston 9a under compressive stress 21 are installed. The release ring 22 inserted into the housing 2a is similarly moved in the axial direction with respect thereto. The smaller sealing portion diameter of the groove sealing ring 20a and the relatively lighter sealing lip produce less moving resistance than the sealing portions engaging the second piston 9a. Unlike Fig. 1, Fig. 2 shows a second piston 8a which is made longer in the axial direction, which is in sealing engagement with the front face of the housing 2a. In addition, the home sealing ring 20 is snap-engaged with the first piston 8a in contrast to the coupling suitable for the shape in FIG.

In still further embodiments of the separating apparatus according to the invention described below, the components corresponding to the first embodiment have the same reference numerals, but partly have different index indices, May be dictated by reference to the description in the embodiment.

Figures 3 and 4 illustrate the separating device 1b complemented by the clutch separating bearing 25b. 3, the clutch separating bearing 25b is fully inserted sideways into the housing 2b for this purpose, the housing corresponding to the contour of the clutch separating bearing 25b and having a groove 27b coming into the interior from the front side 26, Respectively. The clutch separating bearing 25b in the case of the inserted friction clutch occupies this position. The position of the clutch separating bearing 25b shown in Fig. 4 corresponds to the released friction clutch (end position), in which case the clutch separating bearing 25b is moved axially from the housing 2b. The structure of the clutch separating bearing 25b is provided with an inner ring 28b which is in a U-shaped hole pointing outwardly and which is connected to the first piston 8b at one side thereof, (38). In order to obtain a suitable installation for the force, the supporting thin plate 38 is provided with a dish spring 30, which is inserted between the vertical section of the supporting thin plate 38 and the inner ring 28b.

The clutch separating bearing 25b is supported on the friction clutch via an outer ring 29b arranged in the circumference. Not only the inner ring 28b but also the outer ring 29b coincide with each other in the housing 2b over the axial area where these sections 31 and 32 are radially spaced apart to form the installation space 33 And a lubricant for lubricating the roller bodies 34 of the clutch separating bearing 25b may be introduced into the inner space. In this case, the lubricant storage may be arranged not only in the inner ring 28b (see FIG. 3) but also in the outer ring 29b (see FIG. 4) as a reservoir. The inner ring 28b to the outer ring 29b on the opposite side of the lubricant reservoir are provided with carrying grooves 35 for supplying a targeted lubricant through which the lubricant can be guided to the roller bodies 34 have. A thin plate cover 36 fixed to the outer ring 29b so as to fit the shape of the outer space 29b is provided for effective sealing of the installation space 33. The end of the lip seal 36 is connected to the inner ring 28b, The portion 37 is vulcanized and fixed. The region of the flat spring 30 is also provided with a sealing portion 39 which is fixed to the supporting thin plate 38 and which has sealing lips and which is located far from the mounting side of the friction clutch, It touches section.

The separation device 1c shown in Figs. 5 and 6 is highly comparable to the separation device Ib (Figs. 3 and 4). 3 and 4), an enlarged installation space is provided between the inner ring 28c and the outer ring 29c of the clutch separating bearing 25c. The inner ring 28c is fixed with a forming ring 40 which is rotatably supported by the inner ring 28c on the basis of the frictional moment of the bearing through a grip suitable for the shape of the guide projection 46c in the guide groove 47c, . The shaping ring 40c has such a shape that in this case fits the contour of the groove 27c and is partly grasped in the hole 45 of the housing 2c in the case of a separate friction clutch (end position).

The separating device 1d of Figs. 7 and 8 is provided with a clutch separating bearing 25d, whose inner ring 28d is rotated. The structure also shows an outer ring 29d supported on the carrier disc 41d. The separating device is provided with a plurality of stepped transverse sections or a provided carrier disc 41d having an overlapped portion in the region of the supply port of the housing 2d is rotated by the first piston 8d through the snap fitting portion 42 And is fixedly supported. The outer edge of the outer ring 29d of the carrier plate 41d is held in the guide groove 47d of the housing 2d so that the carrier plate 41d is bent at right angles to form the guide protrusion 46d, Is prevented. The outer ring 29d is provided with a curved thin plate 43 which is rotatably fixed with its long radial sides supported by the force of the dish spring 30 so as to be fitted to the carrier circular plate 41d And this enables radial and axial adjustment of the outer ring 29d. A lip sealing portion 37 is used for sealing the annular gap 44 between the inner ring 28d and the outer ring 29d which is in contact with the rotating inner ring 28d and which, Is supported through a thin plate cover (36) fixed to the lower plate (29d).

The separating device 1e according to Fig. 9 shows a groove sealing ring 20e for sealing of the pressure chamber 13, which together with the reinforcement 20f forms one unit. A vulcanized bond is provided in which a rigid, non-separable bond is created for bonding of both components. In this case, the reinforcing portion 20f surrounds a region of the front side of the first piston 8e pointing to the pressure chamber 13 and surrounds the end region of the first piston 8e with a cylinder- . At the free end, the reinforcing portion 20f has a radially inwardly directed snap engagement projection 20g which is supported in the annular groove 20h of the first piston 8e for snap fit to the shape. The reinforcing portion 20f formed from the thin plate through the deep drawing method also has an attachment portion 17 which has a collar 16 arranged radially inwardly in the second piston 9e on the end side Thereby forming the stroke limit of the stopper 15 and accordingly the first piston 8e. Unlike the above-described separating devices, the separating device 1e shows a pressure spring 48e inserted between the housing 2e and the inner ring 28e, whereby the clutch separating bearing 25e and the dish- 30 can be achieved and this allows for the abandonment of the initial load valve. In this case, the pressure spring 48e is formed as a conical spring, which provides reliability against bending and also assures short block length.

Fig. 10 shows a clutch separating bearing 25f which is releasably arranged on the first piston 8f. To this end, the first piston 8f is provided with a bearing fixing portion 49f on the front side, to which the carrier plate 41f is releasably snap-engaged. A pressure spring 48f is supported on the housing side plate 41f and an outer ring 29f of the clutch release bearing 25f is supported on the opposite side. A support disc 50 is provided to indicate the possibility of axial and radial adjustment of the outer ring 29f, which is assisted by the force of the disc-shaped spring 30, ). The short sides arranged at right angles to the long sides of the support disc have sealing portions 50a and abut on the outer ring 29f on the inner side.

Fig. 11 shows a separating device 1g provided with a stroke limiting portion of the second piston 9g. For this purpose, an annular groove 53g for housing the elastic ring 52 is formed inside the housing 2g. An elastic ring 52 is supported in the peripheral groove 54g at the mounting position of the second piston 9g which is formed on the outer surface of the second piston 9g and the longitudinal extension of the second piston 9g has a width It exceeds the number of times. The difference in dimension between the width of the elastic ring and the longitudinal extension of the peripheral groove 54g determines the stroke of the second piston 9g.

12 can lead to a positionally fixed second piston 9h which has one end thereof and is supported on the annular flange 5 of the guide sleeve 6h and has a housing collar 51 with its other end, . The annular flange 5 of the guide sleeve 6h has a plurality of projections 55 arranged around it to which the second piston (not shown) 9h.

The separating device 1i according to Figure 13 shows a second piston 9i which is located by means of an elastic ring 52 which in the annular groove 53i, which is formed in the housing 2i, And is supported in a peripheral groove 54i suitable for the width of the elastic ring 52 at the mounting position of the elastic ring 52. [ The separation device 1i further includes a torsion preventing portion of the inner ring 28i which is provided with a molding ring 40i on the side of the housing, And the guide protrusion is engaged into the guide groove 47i of the housing 2i.

Another alternative bearing fixture of the second piston can be derived from the separator 1j according to Fig. For this purpose, the second piston 9j is formed as an insert part, that is, in the case of the manufacturing method of the housing 2j by the pressure casting method or the plastic injection molding method, the second piston 9j formed in the cylinder shape is directly inserted into the housing 2j ). ≪ / RTI > In order to improve the closed shape between the housing 2j and the second piston 9j, the outer surface of the second piston 9j has two circumferential grooves 54j spaced apart in parallel, These are filled from the material of the housing 2j in the manufacturing process. In order to make a detachable and shape-fit fixation of the clutch separating bearing 25j, they are engaged with the first piston 8j via the bearing fixing portion 49j and, at this end, A retaining ring inserted in the retaining ring 8j is used.

15 and 16 show a separating device 1k, which has a connecting piece 68 which radially escapes from the housing 2k. The connecting piece has two connecting portions, that is, a conduit connecting portion 57 and a discharging connecting portion 58, which are arranged on the end side in parallel spaced apart arrangement, which are arranged at right angles to the connecting piece 68 do. The conduit connecting portion 57 and the discharge connecting portion 58 are guided through the hole 59 of the clutch case 56 and thereby the access from the outside of the clutch case 56 . From Fig. 15 it can be seen that in this case the discharge connection 58 or scavenging connection is arranged so as to be placed at the highest position of the conduit connection 57, i.e. in the highest position of the hydraulic system in the state in which it is installed, It can be seen that the contained air can be effectively discharged when needed.

The connecting piece 68 also has two supply ports 14a and 14b which are spaced apart in the axial direction and which communicate with the outlets 69a and 69b, Drain connection 58. As shown in FIG. For sealing of the supply apertures 14a, 14b, they are effectively sealed by the sphere 66 on the end side, i.e. above the inflow of the outlets 69a, 69b. At the mounting positions of the spheres 66, they are suitably supported in shape by caulking 67 provided radially in the direction of the center of the holes of the supply ports 14a, 14b. For the simple introduction of the sphere 66 into the connecting piece 68, the feeds 14a, 14b are conically expanded on the end side.

17 and 18 show the separating device 11, which can be compared with the configuration of the separating device 1d according to Figs. 7 and 8. Fig. The outer ring collar 63 of the outer ring 291 is supported by the snap ring engaging portion 42 in the vicinity of the outer periphery which is in contact with the vertical section in the carrier circular plate 411 suitably engaged with the shape of the first piston 8d. do. An attenuation ring 61 is inserted in order to obtain the possibility of radial adjustment of the outer ring 291 with respect to the carrier disc 411. This includes a section 64 coaxially arranged with respect to the guide sleeve 6d, And is arranged between the disk 411 and the inner wall of the outer ring collar 63. [ In this case, the damping ring 61 is centered on the section 64 via an elastically formed spring arm 62, which is distributed inwardly and tilted and distributed inward. This configuration of the damping ring 61 results in an attenuated radial deflection of the outer ring 29l relative to the carrier disc 41l. In particular, the damping ring 61 made of plastic is also provided with an axial sealing lip 60 at the front side pointing to the clutch separating bearing 25l, which is formed radially inward, i.e. towards the guide sleeve 6d And this shoulder is sealed under the initial stress and abuts against the vertical section of the carrier disc 411. In the valve section, an additional region which is spaced apart from the inner ring contour in the axial direction or the radial direction is formed in contact with the region, which forms a labyrinth-shaped sealing portion by interaction with the above-mentioned inner ring groove. This effectively prevents the entry of contaminants and the release of lubricants with little and no friction. 18, the structure of the damping ring 61 according to the present invention becomes clearer. This is because, for the purpose of achieving improved elasticity, which facilitates the installation of the damping ring 61 in the outer ring collar 63, And has an axial gap 65 in the axial direction. 18 also shows the inclined arrangement of the spring arms 62 in the installed state of the damping rings 61, which ensures a pre-stressed installation of the spring arms 62 in the carrier disc 41l.

Therefore, the hydraulic separator for a friction clutch according to the present invention as described above can be advantageously manufactured at a cost, has advantages of assembly, and has an excellent effect of maximizing the efficiency of weight as well as the drying space.

Claims (37)

The guide sleeve (6a to 6d) is inserted into the groove of the center of the housing at a distance in the radial direction with respect to the inner wall, and a piston, which is formed as a telescopic piston, Is guided movably in the axial direction while bridging the radial gap between the guide sleeves (6a to 6d) and the inner wall, wherein the piston is sealed with a front side of the piston and a pressure chamber And the other front side of the piston is in contact with the clutch release bearings 25b to 25d, which is at a boundary between the pressure chambers 13 and away from the pressure chambers 13, The friction clutch fluid of the vehicle, which is surrounded by the guide sleeves 6a to 6d and is filled by the pressure medium through the pressure medium supply source In the formula separator, The telescopic piston has a cover-shaped second piston (9a to 9d) formed from a steel plate by a deep drawing method, is sealed through a sealing ring (21) inserted into the housings (2a to 2d) The two pistons 9a to 9d coaxially surround the first pistons 8a to 8d which are movably guided on the guide sleeves 6a to 6d so that the front side of the first pistons 8a- There is provided a groove sealing ring 20 which is arranged in the first pistons 8a to 8d and which is arranged between the guide sleeves 6a to 6d and the first pistons 8a to 8d On the one hand, and on the other hand to sealing between the second pistons (9a-9d) and the first pistons (8a-8d). The method according to claim 1, The groove sealing ring 20e is inseparably engaged with the reinforcing portion 20f wherein the reinforcing portion 20f is supported by the first piston 8e at the front side and is fitted to the first piston 8e, (Fig. 9). ≪ RTI ID = 0.0 > 9 < / RTI > 3. The method of claim 2, Characterized in that the first pistons (8a-8d) have a smaller moving resistance than the second pistons (9a-9d). The method according to claim 1, The guide sleeves 6a to 6d and the second pistons 9a to 9d manufactured by the deep drawing method without cutting are used and these uncoated outer surfaces 7 to inner walls of the groove sealing rings 20 And the sealing lip is guided by the seal member. The method according to claim 1, Characterized in that the second pistons (9a to 9d) form a stopper (19) in the housings (2a to 2d) through a collar (18) pointing radially outward at the end side, . The method according to claim 1, The ends of the second pistons 9a-9d pointing toward the clutch release bearings 25b-25d are provided with a collar 16 pointing radially inwardly and the collar engages the attachment portions with the first pistons 8a-8d ) Of the first piston (8a-8d) in the radial direction and ensures the stroke limit for the first piston (8a-8d). The method according to claim 1, Characterized in that rotationally symmetrical grooves (27b to 27d) are formed in the housings (2a to 2d), the grooves corresponding to the outer contours of the clutch separating bearings (25b to 25d) Device. The method according to claim 1, Characterized in that the inner rings (28b, 28c) of the clutch release bearings (25b, 25c) are fixed to the first pistons (8b, 8c) in a rotationally fixed manner (Figs. 3 to 6). The method according to claim 1, Characterized in that the clutch separating bearings (25d, 25f) have rotating inner rings (28d, 28f) as well as outer rings (29d, 29f) which are fixedly and indirectly engaged with the first pistons Hydraulic separator for clutch (Figs. 7, 8, 10). 8. The method of claim 7, Characterized in that the clutch separating bearings (25f, 25h and 25j) are fixed to the first piston (8f) with the separable bearing fixing portions (49f, 49h and 49j) 10, Fig. 12, Fig. 14). The method according to claim 1, The guide protrusion 46d is formed with a bearing fixing portion for the clutch separating bearing 25d and the guide protrusion 46d is fixed to the first piston 8d through a snap fitting portion 42, Wherein the carrier disc is provided for supporting the outer ring 29d and the guide protrusion 46d pointing radially outwardly provides a frictional moment support for the outer ring 29d Is engaged into the guide groove (47a) in the housing (2d). 12. The method of claim 11, A reinforcing support disc 50 is arranged between the carrier discs 41d and 41f and the disc-shaped spring 30 of the clutch separating bearings 25d and 25f and the support disc is fixed to the outer rings 29d and 29f , And the support disc is supported by the force of the disc-shaped spring (30) and abuts against the vertical section of the carrier discs (41d, 41f) on a large surface. Hydraulic separator for clutch (Figs. 8 and 10). The method according to claim 1, The damping ring 61 fixed to the outer ring collar 63 of the outer ring 291 is inserted into the guide sleeve 6d through the spring arms 62 which are distributed around and resiliently formed, (71) of the carrier disc (41) extending in the radial direction of the carrier disc (41). 14. The method of claim 13, The damping ring 61 has an axial sealing lip 60 guided radially inward and in contact with the vertical section of the carrier disc 41l on the side of the front side pointing to the clutch separating bearing 25l , And a section which is placed on the opposite side and which is complementarily formed axially or radially with respect to an outline suitable for the inner ring (28d), said section comprising a labyrinth-shaped sealing section, or a polished sealing section Wherein the first and second frictional coupling portions form a frictional engagement portion. The method according to claim 1, The sections of the inner ring 28b and the outer ring 29b extending in the axial direction in the direction of the housing 2b and falling at radially spaced intervals form an installation space 33, (Fig. 3 and Fig. 4). 16. The method of claim 15, Characterized in that a reservoir body is formed in the fixed or rotating inner ring 28b or the outer ring 29b and the reservoir body ensures the supply of lubricant to the roller body 34 of the clutch separating bearing 25b Hydraulic separator for friction clutches. 17. The method according to claim 15 or 16, A lubricant is supplied to the roller bodies 34 through the carrier grooves 35 where the carrier grooves 35 are in each case an inner ring 28b or an inner ring 28b which is placed on the opposite side of the lubricant reservoir or storage body And is attached to the outer ring (29b). The method of claim 1, wherein The forming ring 40 fills an annular gap formed between the clutch separating bearing 25c and the housing 2c and in the case of a separate friction clutch the axial section is partly filled into the grooves of the housing 2c And the frictional moment of the inner ring (28c) is supported in the housing (2c) through the shape closing. The method according to claim 1, Characterized in that the second piston (9g to 9j) belongs to a support means, and the support means releases the adjustment distance restriction or the position fixation of the second piston (9g to 9j). 20. The method of claim 19, An elastic ring 52 is inserted into the annular groove 53g in the housing 2g and the elastic ring is positioned in the peripheral groove 54g of the second piston 9g, Characterized in that the longitudinal extension extends beyond the width of the resilient ring (52) (Figure 11). 20. The method of claim 19, Wherein an elastic ring is inserted in the peripheral groove of the second piston and the elastic ring engages in an annular groove of the housing at an installation position wherein the longitudinal extension of the annular groove exceeds the width of the elastic ring To the hydraulic clutch. 20. The method of claim 19, Characterized in that the resilient ring (52) located in the housing (2i) for positioning of the second piston (9i) is located in the peripheral groove (54i) of the second piston (9i) Hydraulic separator for clutch (Fig. 13). 20. The method of claim 19, The second piston 9h is supported on the axially projecting protrusions 55 which are arranged in the annular flange 5 of the guide sleeve 6h locally with one end thereof in the installed position, (Fig. 12) for contacting the housing collar 51 via a collar 16 formed in contact with the other end radially inward. 20. The method of claim 19, Wherein the second piston (9j) is cast directly as an insert part in a pressure casting method or a plastic injection molding method for manufacturing the housing (2j) (Fig. 14). 25. The method of claim 24, In order to fix the second piston 9j in the axial direction, the second piston has at least one circumferential groove 54j which is filled with a casting material in the manufacturing process of the housing 2j And a hydraulic separator for a friction clutch. A guide sleeve (6e to 6k) is inserted in the groove at the center of the housing in a radial spacing relation to the inner wall, and a piston is provided on the guide sleeve between the guide sleeve and the inner wall The piston being guided movably in the axial direction while bridging the radial gap of the pressure chamber (13), wherein the piston is sealed with a front side thereof and forms a boundary of a pressure chamber (13) formed in a circular ring shape, With the other front side of the piston being in contact with the clutch release bearings 25e to 25k which are surrounded by the housings 2e to 2k and guide sleeves 6e to 6k And is filled by a pressure medium through a pressure medium supply source, The piston includes first pistons 8e through 8k and second pistons 9e through 9k formed from a steel plate by a deep drawing technique, which are telescopically arranged coaxially with respect to each other, Wherein a pressure spring (48e to 48k) is inserted between the housing (2e to 2k) and the clutch release bearings (25i to 25k) fixed to the first piston (8e to 8k), and the telescopic Sealing rings (20, 20a, 20e) arranged on the first pistons (8e to 8k) are provided for covering the front side of the first pistons (8e to 8k) for sealing the pistons, On the one hand, the sealing between the guide sleeves 6e to 6k and the first pistons 8e to 8k, on the one hand, and on the other hand, between the second pistons 9e to 9k and the first pistons 8e to 8k, 8e to 8k) And the second pistons 9e to 9k are sealed through a sealing ring 21 inserted in the housings 2e to 2k with respect to the housings 2e to 2k. Hydraulic separator for clutches. 27. The method of claim 26, The first piston 8f belongs to the carrier original plate 41f and the original plate of the carrier contacts the outer ring 29f of the clutch separation bearing 25f at one side and the pressure spring 48f at the opposite side (Fig. 10). 28. The method of claim 27, Characterized in that the carrier original plate (41f) has an attachment portion protruding in an axial direction, and a spring end portion of the pressure spring (48f) is centered on the attachment portion. 27. The method of claim 26, The pressure springs 48e to 48k are formed as conical springs and the spring ends thereof are connected to the housings 2e to 2k and to the clutch release bearings 25e to 25k to the carrier & And is supported on the disk (41f). 27. The method of claim 26, Characterized in that the housing (2k) integral with the connecting piece (68) projecting in the radial direction from the direction of the outer wall of the clutch case (56) can be supplied to the separating device via the compression medium Device. 31. The method of claim 30, Characterized in that the connecting piece (68) is provided at its free end with a discharge connection (58) and a conduit connection (57), which are arranged at right angles to the connecting piece (68) Hydraulic separator for clutches. 32. The method of claim 31, The connection pieces 68 are arranged with two supply ports 14a and 14b extending parallel to each other and the supply ports are connected to the discharge ports 69a and 69b formed in the conduit connection 57 and into the discharge connection 58, , 69b of the friction clutches. 33. The method of claim 32, Characterized in that the supply ports (14a, 14b) are sealed in each case by a closing part formed as a sphere (66). 33. The method of claim 32, Characterized in that the feed openings (14a, 14b) extend conically at the end side and the sphere (66) is suitably supported in shape by a cowling (67) adapted to the shape in each case at the mounting position Hydraulic separator for friction clutches. 31. The method of claim 30, And the conduit connecting portion (57) is arranged to be moved with respect to the discharge connecting portion (58). 31. The method of claim 30, Characterized in that said housing (2k) and connecting piece (68) are formed as one piece, wherein these units are made of aluminum. 34. The method according to claim 32 or 33, The connecting piece 68 having the conduit connecting portion 57 and the discharging connecting portion 58 is arranged on the peripheral side of the housing 2k with respect to the pressure chamber 13 and therefore the assembling of the separating devices 1a to 1k Wherein the discharge of the discharge connection (58) at a position of the pressure chamber (13) flows into the highest point of the pressure chamber (13).