KR19990028286A - Hydraulic restraint device for friction clutch - Google Patents

Abstract

The present invention relates to a hydraulic restraining and releasing device for a friction clutch in an automobile having a single case, wherein a guide pipe is inserted in a groove in the center of the case at a radial distance from the inner wall. The piston, formed as a telescopic piston on the top, is guided to move axially while bridging the radial gap between the guide pipe and the inner wall. According to this invention, a restraining and releasing device 1b is provided in order to obtain a structural method for reducing the required drying space, and the restraining and releasing device has a secondary piston 9b formed in a sheath shape, and the secondary piston Coaxially surrounds the primary piston 8b guided to move on the guide coating 6b.

Description

Hydraulic restraint device for friction clutch

The restraint and release device of the above kind is known from JP3-186620-A. The structure of the restraint and release device comprises a telescope piston, which consists of two separate pistons, which can move coaxially to one another in an end position. The hollowed piston then has a relatively large wall thickness, which adversely affects the required radial structural space of the device. On the pressure chamber side, each piston is also provided with a radially outwardly attached portion, which is formed with an annular groove for accommodating the seal. In this case, the radial inner piston contacts the inner wall of the outer piston and the outer piston contacts the hole wall of the case. Another seal was provided for sealing the annular gap between the guide coating of the case and the inner wall of the inner piston. The known restraint and release device has a large component range with the consequences of the disadvantages of the cost in addition to the disadvantages of the drying space.

The object of this invention is therefore to make a hydraulic restraint and release device which can be advantageously manufactured and has the advantages of assembly, and the drying space is also optimal in weight.

The present invention relates to a hydraulic restraint, release device for a friction clutch by the features of the higher concept of claims 1 and 29.

Further details of this invention can be seen in the following description of four embodiments in eight figures in total:

1 is a half sectional view of an acceptance cylinder case in which the telescopic piston according to the invention is shown in a pressure-filled state;

FIG. 2 shows an acceptance cylinder case corresponding to FIG. 1 with a different primary piston seal; FIG.

FIG. 3 shows a restraining and releasing device arranged in a primary piston, having a circumferential outer ring and having a clutch moving bearing at a restrained end position, in a half section,

4 shows the restraint, release device according to FIG. 3 in a released position (end position),

FIG. 5 shows a restraining and releasing device having a take-up cylinder case with optimized drying space in the axial direction, indicated at the end position where the clutch moving bearing is restrained in the restraining and releasing device,

FIG. 6 shows the restraint, release device shown in FIG. 5 in the unlocked position (end position), FIG.

7 shows a restraint and release device having a half-section, having an inner ring in which the clutch movement bearing of the restraint and release device rotates,

8 shows the restraint, release device according to FIG. 7 in the released position (end position) of the clutch movement bearing,

9 shows a restraining and releasing device in which a groove sealing ring is provided for sealing the pressure chamber, the groove sealing ring being used through such a reinforcing portion having a reinforcing portion and the groove sealing ring snap-fitted to the primary piston suitable for the mold.

10 shows the structure of the restraint and release device according to the present invention in which a compression spring is inserted to remove the preliminary pressure valve between the case and the carrier disc belonging to the clutch moving bearing.

11 shows the administrative limitations of the secondary piston of the restraining and releasing device according to the present invention,

12 shows the secondary piston inserted in a fixed position between the guide coating and the case,

FIG. 13 shows the elastic stop ring inserted in the case, positioned in the circulation groove of the secondary piston, to reach the positional fixation of the secondary piston;

14 shows a secondary ring suitably injected into the case,

Figure 15 shows the restraint, release device is installed in the conduit- and scavenging portion coming out of the case in a radial bar,

FIG. 16 shows a sectional view taken along line B-B of the restraint and release device according to FIG. 15;

FIG. 17 is a longitudinal sectional view of the restraint and release device showing the deformation of the restraint and release device shown in FIG.

FIG. 18 shows a sectional view taken along the line A-A from FIG.

The above problem is solved by the features mentioned in the characterizing part of claims 1 and 28.

The hydraulic restraint and release device constructed in accordance with this invention has a secondary piston formed in the shape of a sheath for the formation of a telescopic piston, the secondary piston being coaxially enclosed in contact with the primary piston. The primary piston is guided over its inner diameter in the guide coating and the secondary piston over the outer surface of the secondary piston in the casing of the restraint and release device. Said piston arrangement allows for a short, axial configuration which is desired in an advantageous manner. Cases that have been guided by conventional structures with pistons in addition to the guiding cladding through almost the entire working stroke have been guided, resulting in reduced weight in the direction of the construction, and thus weight- and cost advantages. This is regulated. The piston according to this invention also improves handling due to the reduced construction length, which can simplify assembly.

2 and 3, in order to seal the secondary piston in the case, there is provided a sealing portion which comes into contact with the outer surface of the secondary piston by prestress. For the sealing of primary pistons, it is provided with a sealing ring, a special groove sealing ring on the front side, and the sealing lip features of the groove sealing ring arranged at both edge regions of the sealing ring, on the one hand, on the outer surface of the guide coating. And on the other hand are sealingly in contact with the inner wall of the secondary piston.

A groove sealing ring arranged in contact with one reinforcing part is inseparably used according to claim 4 for the purpose, and this reinforcing part is again snap-bonded to the annular piston to suit the mold. For this purpose, such a vulcanization is advantageously presented, with vulcanization and both components are assembled into one unit. As an alternative, the invention contemplates such a groove sealing ring in which the reinforcing portion is partially enclosed as a sealing material in the groove sealing ring, and the reinforcing section coming out of the groove sealing ring is fixed to the annular piston.

According to claim 5 this invention ensures that the primary piston has a smaller resistance to movement than the secondary piston. The above method of operation is obtained due to the smaller sealing diameter of the groove sealing ring installed for the primary piston as compared to the seal inserted in the casing for sealing the secondary piston. In addition, the relatively weak sealing lip features of the groove sealing ring exert a smaller friction than the sealing ring guided in the case while contacting the outer surface under prestress for sealing the secondary piston. In the case of the operation of the restraint and release device according to the present invention, which is brought about by the operation of the clutch pedal, by means of different movement resistance, the movement of the primary piston is first made before the movement of the secondary piston.

According to claim 6, it is suitable for the purpose to manufacture the guide pipe and the secondary piston without cutting by the deep drawing method. In addition, the present invention uses for drawing and releasing devices which can advantageously produce the above-mentioned costs, for example after gas nitriding and after honing brushing or polishing and subsequent intermediate treatment with chlorination as corrosion protection. This allows the costly surface layer formation which is conventionally conventional in the guide holes of the case to be eliminated.

The arrangement of the restraining and releasing device according to the present invention according to claims 7 and 8 is such that the secondary piston is formed with a stopper via a collar pointing radially outward in one direction to the case (claims) Scope 7). In order to make the stroke limit of the primary piston, according to claim 8, a collar is installed in which the secondary piston is pointing inward in the radial direction, and the collar covers and grips the attachment in the primary piston and thus 1 To form administrative limits on the chartistones

Emphasizing a compact structure, according to claim 9, the case is formed with a groove which is generally rotationally symmetrical, in which the clutch movement bearing can be accommodated in the case of the restrained position of the friction clutch. Can be.

The construction of this invention according to claims 10 and 11 relates to the formation of the inner and outer rings of the clutch movement bearing. According to claim 10, the restraining and releasing device according to the present invention is provided with an inner ring fixedly rotatable to the primary piston and a rotatably arranged outer ring of the friction clutch. On the contrary, the configuration according to claim 11 has an outer ring which is indirectly coupled to the primary piston in a non-rotating manner, and a rotating inner ring.

In order to make a separable fixation of the clutch movement bearing, a separable bearing fixation is provided according to claim 12 suitable for the mold between the primary piston and the bearing of the clutch movement bearing. The above arrangement makes it possible to replace the damaged parts of the hydraulic restraint and release device, if necessary, without needing to replace the case and the clutch moving bearing jointly in case of damage.

According to claim 13, a carrier disc is installed between the primary piston and the outer ring arranged in such a way that the clutch movement bearing is not rotated, where the carrier disc is formed in a mold to achieve a simple and cost-effective assembly. It is fixed to the primary piston via a suitable snap.

In order to make an effective seal between the inner ring and the outer ring of the clutch moving bearing, claim 14 is a reinforced support disc, which is assisted by the force of the disc spring to contact over a large area in the vertical section of the bearing inner ring. Is installed. The support disc according to this invention effectively prevents unfavorable lubrication of the lubricant from the clutch moving bearings and also enables the axial and radial adjustment of the outer ring. The above measures favor the service life of the clutch moving bearing.

According to claim 15 it is suitable for the purpose to insert a damping ring between the outer ring and the carrier disc which is damped, i.e. inhibits radial movement, which avoids large radial deviations of the outer ring. In accordance with this invention, a damping ring is provided for this purpose which is fixed to the outer ring collar of the outer ring, which damping ring is contacted over the concentric section of the guide coating via spring arms which are distributed around and elastically made. have. The damping ring, preferably made from plastic, has a plurality of elastic spring arms distributed around and bridging one radial gap, which spring arms allow for a limited radial deviation of the outer ring from the clutch movement bearing. Let's do it.

In one advantageous configuration of the damping ring, the claim 16 is adapted to provide the damping ring with a sealing lip in the axial direction on the side which points at the clutch moving bearing at the front side. This axial sealing lip is a radially inwardly facing shoulder, integrally formed with the damping ring, and radially inwardly contacted when sealed to the vertical section of the disc of the carrier under prestress. have. The valve section is provided with a range corresponding to the inner ring contour, which is complementary to the corresponding inner ring section, forming a labyrinth seal to avoid lubricant loss.

In another advantageous configuration of the invention according to claim 17, the inner ring and the outer ring, respectively, are radially spaced apart from each other and have sections facing the case, whereby the resulting dry space It can be formed as a lubricant reservoir for lubrication of the roller body of the clutch moving bearing. In accordance with claim 18 a lubricant filled reservoir body can be inserted into the drying space, wherein the reservoir body is secured to the fixed or rotating inner or outer ring of the clutch moving bearing for the lubricant supply of the roller body. It may be arranged. According to claim 19, conveying grooves are formed for a desired supply of lubricating material, which are then arranged in inner to outer rings which are then situated opposite to the reservoir body of the lubricant reservoir.

This inventive concept according to claim 20 fills the annular gap which is adjusted between the case and the clutch movement bearing in the case of the released friction clutch and in the case of the released friction clutch protrudes into the corresponding groove of the case. Arranging the rings. This advantageous configuration effectively prevents the ingress of dust into the case and into the clutch symmetrical bearing and into the rotationally symmetric groove into the guide passage between the primary and secondary pistons.

In accordance with claim 21 it may be advantageous that the support means belonging to the secondary piston causing the positioning of the secondary piston or the restriction of distance adjustment. The above configuration enables, for example, multiple use of secondary pistons, thereby contributing to cost reduction and limiting component diversity. In this case, the suitability of the maximum piston stroke by limiting or fixing the secondary piston is considered in accordance with this invention. The invention according to claim 22 is made so that the elastic stop ring is inserted into the case in the annular groove, which is located in the peripheral groove of the secondary piston in the installed state, where the longitudinal direction of the peripheral groove is The extension exceeds the width of the elastic stop ring and thereby adjusts the stroke limitation of the secondary piston. As an alternative, the claim 23 according to claim 23 is located in the installation position into the annular groove of the case, wherein the width of the annular groove is in the peripheral groove of such a secondary piston which exceeds the width of the elastic stop ring. The elastic stop ring is inserted into the

In order to realize the simple positioning of the secondary piston, the present invention provides an elastic stop ring seated in the case according to claim 24, which has a periphery of the secondary piston suitable for the width of the elastic stop ring. It is located in the groove.

An alternative positional fixation of the secondary piston is provided by claim 25 in which the secondary piston is supported at its installation position with its one end supported by the annular flange of the guide coating and with its other end It is in contact with the case collar via a collar formed inward in the direction. In order to create a sufficient transverse cross section within the range of the annular flange, the annular flange is provided with protrusions protruding axially in the contact range of the secondary piston, and the secondary pistons are supported on the protrusions.

Claim 26 claims that the secondary piston is directly recast from the case material as an insert in pressure casting or plastic die casting for the manufacture of the case, thereby simultaneously positioning the secondary piston. According to the above-mentioned processing method, the hole for accommodating the secondary piston is eliminated in an advantageous manner. In accordance with claim 27, the outer surface of the secondary piston has at least one peripheral groove for optimizing the position fixation, which is filled by the injection material in the manufacturing process of the case.

According to claim 28, the invention has made an arrangement of compression springs for the maintenance of the preload between the clutch shift bearing and the clutch adjustment spring. The structure according to the invention consists of a primary piston and a secondary piston, which comprise such pistons which are arranged coaxially to be longitudinally movable relative to one another and which form one telescopic piston. According to this structural shape, the clutch moving bearing is fixed to the primary piston, and the compression spring is inserted between the case and the bearing ring of the clutch moving bearing. The structure according to this invention above does not require a preliminary pressure valve and thereby represents a cost reduction. In addition, fewer component circumferences were associated with the slight disturbance of restraint and release devices.

An advantageous configuration is provided with a carrier disc belonging to the primary piston according to claim 29, which is supported by a clutch moving bearing on one side and a compression spring on the opposite side. According to claim 30, an attaching portion is provided in which the carrier disc protrudes in the axial direction, and the spring end of the compression spring is in contact with the preliminary stress. In addition to this, the idea allows the attachment to center the spring end internally or externally.

Conical springs are installed in accordance with claim 31 to create an advantageous short construction length of the compression spring, which further provides safety against adverse bending and then no guidance is necessary.

It is helpful for the purpose to install a case for the restraint and release device according to claim 32, which is made integrally with a joint projecting radially from the clutch case or in the direction of the outer wall of the clutch case. have. The joints, which can also be marked as fused pipes, can additionally eliminate the need for costly assembly of pipe conduits; In addition, the number of joints to be sealed is reduced, i.e. the pipe screw coupling in the direct casing is eliminated and the required alignment of the pipe conduits can be lost during assembly, resulting in cost savings.

In an advantageous configuration of the invention according to claim 33, a separate scavenging connection or an exhaust connection is included in the conduit connection, which simplifies the first acceleration of the hydraulic system during the initial assembly of the pressure restraint and release device. And possibly later exhaustion of the system can also be effected effectively. According to the preferred configuration of the junction, the free end is provided with an exhaust connection and a conduit connection, wherein the connections are spaced in parallel and arranged at right angles to the junction. The joints are guided through the opening of the clutch case in the installed state of the restraint and release device according to the present invention, with the result that simple joining possibilities exist.

According to claim 34, the joints are available via two supply holes which are parallel to each other, which supply holes are identical with the discharge holes made in the conduit connection and in the exhaust connection. In order to achieve an effective sealing of the supply holes, claim 35 is intended to seal it with a separate closure part, ie a sphere, at the end side.

A longitudinal hole is conically widened at the end side in accordance with claim 36 for simplified transfer of the sphere into the longitudinal holes. After reaching the end position, a tightening is also made which is suitable for the mold of the wall range of the longitudinal hole, which ensures a limited radial cover of the sphere, whereby the sphere is supported for the mold.

According to claim 37, as an alternative to the parallel arrangement, also the shifted arrangement of the conduit connection and the exhaust connection is formed depending on the pre-determined installation rate, where the desired junction occupies the highest installation position in the calculation. So that they are arranged.

This idea includes the construction of one side of the case and of the joint according to claim 38. The unit can in this case be advantageously manufactured as a cast product, for which aluminum pressure casting is particularly suitable.

1 and 2 show the structure of the restraining device 1a of the present invention, respectively, in a half-sectional cross-sectional view in a state of under pressure. The restraining and releasing device 1a has one case 2a, which is fixed to a transmission case not shown in FIGS. 1 and 2 in a state where it is installed via the front side 3. In the case 2a, a plurality of stepped grooves 4 are formed to be rotationally symmetrical in the center. A guide coating 6a centered through the annular flange 5 on the front side 3 extends in the groove 4 while maintaining a radial gap with respect to the groove 4 of the case 2a. . In Figs. 1 and 2, the pressure axis extending in the guide coating 6a is not shown, and this input shaft connects the friction clutch with the variable speed transmission. The primary-piston is guided on the outer surface of the guide coating 6a, where the primary piston 8a contacts the guide coating 6a in the radial direction via a narrowly designed gap. The primary piston 8a is provided with a groove 24 for lubricating oil in one hole wall. The primary piston 8a having an annular cylindrical shape is movable in the axial direction on the guide coating 6a. The secondary piston 9a coaxially surrounding the primary piston 8a is inserted into the groove 4 of the case 2a so as to be movable in the axial direction. The overlapping portion 10 which is in contact with one step 11 of the recess 4 and formed in the annular flange 5 is used for centering the guide coating 6a. This guide coating 6a is also used for receiving the support ring 12, and an unmarked shaft sealing ring can be inserted into the support ring. The support ring 12 has a stepped shape and is centered in the guide coating 6a. The support ring 12 contacts the annular flange 5 via a vertical section. This primary piston 8a can be freely made via the conveyance port 23 at its end facing the friction clutch on its outer surface, which conveyance interacts with the collar 16 of the secondary piston 9a. .

The pressure chamber 13, which is surrounded by the case 2a, the guide coating 6a, the primary piston 8a and the secondary piston 9a, passes through a single supply hole 14 to supply the source of the pressure medium. Connected with The pressure action of the pressure chamber 13 results in the axial movement of the primary piston 8a and of the secondary piston 9a where the deposits in the primary piston 8a are due to the different resistance of movement of both pistons. Axial movement of the primary piston 8a first until the primary piston reaches the stopper 15 formed by the rotating collar 16, covering (17) from above and pointing inward in the radial direction. This is done. Synchronous axial movement of the secondary piston 9a then takes place until the collar 18 facing outward in the radial direction of the secondary piston contacts the case 2 which collectively forms the stopper 19. In the case of reversing the piston movement, firstly, the primary piston 8a is again in contact with the collar 16 of the second piston 9a until the conveyance port 20 inserted outside from the primary piston 8a comes into contact with the collar 16. And then both pistons are moved to the end position, which is in contact with the collar 18 to the annular flange 5. The different transfer resistance between the primary piston 8a and the secondary piston 9a is determined by the sealing of both pistons, which produce different frictional forces, in particular due to the different sealing diameters.

The primary piston 8a is provided with a groove sealing ring 20a whose sealing lip features are in contact with the guide coating 6a on the one hand and the secondary piston on the other hand. The sealing gap between the secondary piston 9a and the case 2a starts from the pressure chamber 13 and is first inserted into the circulation groove of the case 2a and is in contact with the secondary piston 9a under compressive stress. 21 is provided. On the other hand, the peeling ring 22 moved in the axial direction and inserted in the case 2a similarly is arranged. The smaller seal diameter and the relatively soft seal lip feature of the groove sealing ring 20a produce less transfer resistance than the seals that engage the secondary piston 9a. Unlike FIG. 1, FIG. 2 shows the secondary piston 8a made longer in the axial direction, and the secondary piston is coupled to the front surface of the case 2a. In addition, the groove sealing ring 20 is snapped to the primary piston 8a in contrast to the coupling suitable for the type in FIG. 1.

In further embodiments described in the following release of the release device according to the present invention, the components consistent with the first embodiment have the same number but in part make the different index index small, resulting in the specification. With regard to the above, reference may be made to the description in the first embodiment.

3 and 4 show the restraint release device 1b that is complemented by the clutch movement bearing 25b. In FIG. 3, the clutch movement bearing 25b is fully inserted laterally into the case 2b. For this purpose, the case corresponds to the contour of the clutch movement bearing 25b and opens the groove 27b coming in from the front side 26. Have The clutch moving bearing 25b in the case of the inserted friction clutch occupies this position. The position of the clutch movement bearing 25b shown in FIG. 4 corresponds to the released friction clutch (end position), in which case the clutch movement bearing 25b is moved axially from the case 2b. The above-described structure of the clutch moving bearing 25b has one inner ring 28b, which has a U-shape which points outwardly of the support plate 38 coupled to the primary piston 8b on one side. It is held in the opening. In order to obtain a suitable contact with the force, the support plate 38 is provided with a single plate spring 30, which is inserted between the vertical section of the support plate 38 and the inner ring 28b. .

The clutch movement bearing 25b is supported by the friction clutch via the outer ring 29b arranged around. While the inner ring 28b and the outer ring 29b coincide with each other, the inner ring 28b and the outer ring 29b extend in the case 26 over the axial range, in which the sections 31 and 32 are spaced radially apart from the installation space 33. Lubrication can be introduced into the inner space for lubrication of the active body of the clutch moving bearing 25b. In this case lubricant storage as a reservoir may be arranged in the inner ring 28b (see FIG. 3) and in the outer ring 29b (see FIG. 4). Transfer grooves 35 are formed in the inner ring 28b to the outer ring 29b opposite the lubricant reservoir for the desired lubricant supply, through which the lubricant is guided to the active bodies 34. In order to effectively seal the installation space 33, a thin plate coating 36 fixed to the outer ring 29b is provided on the outside to suit the mold, and the thin plate coating is narrow to the inner ring 28b at the end side. The lip shaped body 37 is vulcanized and fixed. In the range of the dish-shaped spring 30, a seal 39 fixed to the support thin plate 38 is provided, and the seal has a sealing lip shape and is located far from the contact side of the friction clutch. Contact the vertical section.

The restraint and release device 1c shown in FIGS. 5 and 6 is very comparable to the restraint and release device 1b (FIGS. 3 and 4). An enlarged installation space is formed between the inner ring 28c and the outer ring 29c of the clutch movement bearing 25c as a difference with respect to the clutch movement bearing 25b (FIGS. 3 and 4). The shape ring 40 is fixed to the inner ring 28c, and the shape ring 40 is caused by the friction moment of the bearing by the grip suitable for the shape of the guide protrusion 46c into the guide groove 47c. Prevents accompanying rotation of the inner ring 28c. This shaped ring 40c is in this case suitable for the contour of the recess 27c and has a shape which is partially gripped into the opening 45 of the case 2c in the case of a released friction clutch (end position). .

The restraint release device 1d in Figs. 7 and 8 is provided with a clutch moving bearing 25d, and rotates the inner ring 28d of the clutch moving bearing. This structure also shows the outer ring 29d supported by the carrier disk 41d. The outer ring 29d supported by the carrier disk 41d having a plurality of stepped cross sections or having an overlapping portion in the range of the supply hole of the case 2d is shown. The carrier disk 41d, which has a plurality of stepped cross sections or has an overlapping portion in the range of the supply hole of the case 2d, is supported by the primary piston 8d in a non-rotating manner via the snap bonding 42. . Outwardly, the carrier disk 41d has a right angled corner (Abkantung) for the formation of the guide protrusion 46d, and the guide protrusion is gripped into the guide groove 47d of the case 2d and thereby the outer ring ( 29d) is prevented from accompanying rotation. The outer ring 29d is provided with a bent thin plate 43 so as not to rotate, and this bent thin plate has its long and radial side and is supported by the force of the dish-shaped spring 30 to suit the force. This curved sheet is in contact with 41d and enables the radial and axial adjustment of the outer ring 29d. In order to seal the annular gap 44 between the inner ring 28d and the outer ring 29d, a thin-covered coating which contacts the surrounding inner ring 28d and is fixed to the outer ring 29d appropriately for the mold ( A lip seal 37 that is supported via 36 is used.

The restraint release device according to FIG. 9 shows the groove sealing portion 20e for sealing the pressure chamber 13, which forms a unit with the reinforcing portion 20f. For the joining of both components, vulcanization is provided, which creates a bond that cannot be separated continuously. In this case, the reinforcement part 20f surrounds the range which points toward the pressure chamber 13 side of the front side of the primary piston 8e, and has a cylindrical section and grips the end range of the annular piston 8e. do. At the free end, the reinforcing portion 20f has a snap-fitting nose portion 20g radially inwardly directed and the snap-fitting nose portion 20h of the primary piston 8e for snap-fitting suitable for the type. Is supported). The reinforcement part 20f molded from the thin plate by the deep drawing method has another attachment part 27, which is arranged radially inward from the secondary piston 9e at the end side. The stopper 15 is drawn with the collar 16 thus forming the lifting limit of the primary piston 8c. Unlike the above-described restraint and release device, the restraint and release device 1e shows a compression spring 48e inserted between the case 2e and the inner ring 28e. With this compression spring, a clutch moving bearing is used. The maintenance of the initial load (vorlast) between 25e and the dish-shaped spring 30 can be obtained, which makes it possible to avoid the initial load valve. In this case, this compression spring 48e provides certainty of bending prevention and otherwise ensures block length.

10 shows the clutch movement bearing 25f detachably arranged in the primary piston 8f. For this purpose, the bearing fixing part 49f is provided in the front surface of the primary piston 8f, and the carrier body plate 41f is snap-attached detachably. The carrier spring 41f is supported by the compression spring 48f on the case side and on the opposite side by the outer ring 29f of the clutch moving bearing 25f. In order to show the possibility of adjustment of the outer ring 29f in the axial direction and the radial direction, a support disc 50 is provided, which is supported by the force of the dish-shaped spring 30, thereby providing a long side. To the vertical section of the carrier original plate 41f. The short side supported at right angles to the long side of the support disc has a sealing portion 50a and contacts the outer ring 29f from the inside.

FIG. 11 shows the restraining and releasing device 1g in which the lifting limit of the secondary piston 9g is provided. For this purpose, one annular groove 53g is placed in the case 2g for accommodating the elastic stop ring 52. In the installation position of the secondary piston 9g, an elastic stop ring 52 is supported in the circulation groove 54g, which is formed in the outer surface of the secondary piston 9g and its longitudinal extension More than several times the width of the elastic stop ring. The difference in dimensions between the width of the retaining ring and the longitudinal extension of the circulation groove 54g determines the stroke of the secondary piston 9g.

In Fig. 12, the fixed position of the secondary piston 9h can be seen, which is supported by the annular flange 5 of the guide coat 6g with its one end and the case collar with the other end thereof. (51) is in contact. In order to achieve the entry of the compressed medium into the pressure chamber 13, the annular flange 5 of the guide coating 6h is formed with a plurality of protrusions 55 arranged around the secondary piston 9h. ) Is supported.

The restraining and releasing device 11 according to FIG. 13 shows a secondary piston 8i positioned by an elastic stop ring 52, which is introduced into the case 2i, whereby the secondary piston It is supported into the annular groove 53i at the installation position of 8I, and into the circulation groove 54i suitable for the width of the elastic stop ring 52. The restraint and release device 1i is also provided with a torsion preventing portion of the inner ring 28i. The inner ring is provided with a shape ring 40i on the case side, and the inner ring has a shape ring on the case side. A 40i is provided, and the shaped ring is bent from one side to the other to form the guide protrusion 46i, and the guide protrusion is bitted into the guide groove 47i of the case 2i.

Another alternative to the secondary piston is the locking mechanism, which can be seen in the restraint and release device 1j according to FIG. For this purpose, the secondary piston 9j is formed as an insert part, that is, in the case of the manufacturing method of the case 2j by the pressure casting method or the plastic die casting method, the secondary piston 9j formed in the cylindrical shape is directly the case 2j. Surrounded by materials. In order to improve the closing shape between the case 2j and the secondary piston 9j, the outer surface of the secondary piston 9j has two peripheral grooves 54j spaced in parallel and spaced therein. Are filled by the material of the case 2j in the manufacturing process. Detachable of clutch moving bearing 25j, in order to make fitting suitable for mold, it is combined with primary piston 8j via position fixing part 49j, for which it is suitable for mold and primary piston at end side The retaining ring inserted in (8j) is used.

15 and 16, the restraint and release device 1k is shown, which has a connecting piece 68 extending out of the case 2k in the radial direction. This connecting piece has joints arranged at parallel intervals on the end side, a conduit joint 57 and an exhaust joint 58 which are arranged at right angles to the connecting piece 68. With the restraint and release device 1k installed, the conduit connection 57 and the exhaust connection 58 are guided through the opening of the clutch case 56, thereby enabling access from the outside of the clutch case 56. . In this case, from Fig. 15, the exhaust connecting portion 58 to the scavenging connecting portion are arranged so as to be placed on the uppermost portion of the conduit connecting portion 57, i.e., at the highest position in the calculation of the hydraulic system. It can be seen that the air contained in the system can be effectively evacuated if necessary.

In addition, the connecting piece 68 is formed with two supply holes 14a and 14b which are arranged spaced apart in the axial direction, and these supply holes correspond to the discharge holes 69a and 69b, These small holes enter the conduit connection 57 to the exhaust connection 58. For the sealing of the supply holes 14a, 14b they are effectively sealed with a sphere 66 on the end side, i.e. on top of the inlet of the discharge holes 69a, 69b. At the installation position of the sphere 66, it is suitably supported by the mold by a wedge clamp 67 formed radially in the direction of the hole center of the supply holes 14a, 14b. The supply holes 14a and 14b are conically widened at the end side for simple introduction of the sphere 66 into the connecting piece 68.

17 and 18 show the restraining and releasing device 11 as compared with the configuration of the restraining and releasing device 1d according to FIGS. 7 and 8. The outer ring collar 63 of the outer ring 29l is located near the outer periphery adjacent to the vertical section on the carrier disk 41l, which is suitably coupled to the primary piston 8d by the snap adhesive portion 42. Supported. The damping ring 61 is inserted in order to obtain the possibility of adjusting the radial direction of the outer ring 29l with respect to the carrier body 41l, and the braking ring has a section 64 coaxially arranged with respect to the guide coating 6d, It is arranged between the carrier body plate 41l and the inner wall of the outer ring collar 63. In this case, the braking ring 61 is centered in the section 64 via the elastically formed spring arms 62 which are distributed around and inclined inward. The above formation of the damping ring 61 results in attenuated radial deflection of the outer ring with respect to the carrier disc 41l. In particular, the damping ring 61 made of plastic is also provided with an axial sealing lip shape 60 on the front side of the clutch moving bearing 25l. It has a shoulder formed radially toward, and the shoulder is in contact with the vertical section of the carrier disk 41l under initial stress. A valve section is provided with a supplementary range formed apart from the inner ring contour in the axial to radial direction, which forms a labyrinth seal in interaction with the inner ring section. This effectively prevents the ingress of contaminants and also the discharge of lubricating materials and reduces friction. From Fig. 18 the structure of the damping ring 61 according to this invention becomes clearer, which is to achieve an improved elasticity which facilitates the installation of the damping ring 61 in the outer ring collar 63. , To create axial voids 65 on the outside. 18, the inclined arrangement of the spring arm 62 is shown with the damping ring 61 installed, which ensures the prestressed contact of the spring arm 62 on the carrier disc 41l. .

The cost is favorable in the automobile industry, and it can be used for hydraulic restraining and releasing device, which has the advantage of assembling and the dry space is optimal.

Claims (38)

Guide grooves 6a to 6d are inserted in the grooves in the center of the case in a radial direction with respect to the inner wall, and pistons are formed as telescopic pistons on the guide coatings, thereby providing guide coatings 6a to 6d. And axially movably guided, crosslinking the radial gap between the inner wall and the inner wall, wherein the piston bounds the pressure chamber 13 sealed with its one front side to form a circular ring shape and Far from the pressure chamber 13, it has contact with the clutch moving bearings 25b to 25d with the other front side of the piston, where the pressure chamber 13 is the case 2a to 2d and the guide coatings 6a to 6d. A friction clutch of an automobile, which is enclosed by and has one such case (2a to 2d) that can be filled by a pressure agent via a pressure medium source In the hydraulic restraint, release device for, The telescopic piston has secondary pistons 9a to 9d formed in a sheath shape, which secondaryly coaxially surrounds the primary pistons 8a to 8d movably guided on the guide coatings 6a to 6d. Hydraulic restraint, release device characterized in that. The method of claim 1, A hydraulic restraining and releasing device, characterized in that the secondary pistons (9a to 9d) are sealed via a sealing ring (21) inserted into the annular groove of the case (2a to 2d). Covering the front side of the primary pistons 8a to 8d, the groove sealing portion 20 arranged on the primary pistons 8a to 8d passes through the sealing lip shape and the sealing gap of the guide coatings 6a to 6d. A hydraulic restraint characterized by a seal between the primary pistons 8a to 8d on the one hand and the secondary pistons 9a to 9d and on the other hand between the primary pistons 8a to 8d, Release device. The method of claim 3, The groove sealing portion 20e is coupled with the reinforcing portion 20f so as to be inseparable, where the reinforcing portion 20f is supported by the primary piston 8e at the front side and snaps to it to suit the mold. Hydraulic restraint, release device characterized in that bonded (Fig. 9) The method according to any one of claims 2 to 4, A hydraulic restraint and release device, characterized in that the primary pistons (8a to 8d) have a smaller movement resistance than the secondary pistons (9a to 9d). The method of claim 1, Guide coatings (6a to 6d) and secondary pistons (9a to 9d) manufactured by the deep drawing method without cutting snow are used, and groove sealing portions 20 are formed on the uncoated outer surfaces 7 to the inner walls thereof. Hydraulic restraint, release device characterized in that the guided upper body of the seal lip. The method of claim 1, A hydraulic restraint and release device, characterized in that the secondary pistons (9a to 9d) form a stopper (19) on the cases (2a to 2d) via a collar (18) pointing radially outwardly on the end side. The method of claim 1, At the ends of the secondary pistons 9a to 9d, which point to the clutch movement bearings 25b to 25d, a collar 16, which points inward in the radial direction, is formed, which is the primary pistons 8a to 8d at the attachment portion. ) Hydraulic restraint, release device characterized in that the radially covered in the gripping to ensure the stroke limit for the primary piston (8a to 8d). The method of claim 1, A hydraulic restraining and releasing device, characterized by casings (2a to 2d) corresponding to the outer contour of the clutch ear bearings (25b to 25d) and generally having rotationally symmetric grooves (27b to 27d) formed therein. The method of claim 1, A hydraulic restraining and releasing device characterized by primary pistons (8b, 8c) in which inner rings (28b, 28c) of clutch moving bearings (25b, 25c) are fixed to primary pistons without rotation. The method of claim 1, Features a clutch moving bearing 25d, 25f having outer rings 29d, 29f engaged indirectly with primary pistons 8d, 8f, and having rotating inner rings 28d, 28f. Hydraulic restraint, release device (Fig. 7, Fig. 8, Fig. 10). The method of claim 9, Hydraulic restraining and releasing device characterized by clutch moving bearings 25f, 25h, and 25j fixed with primary fixing pistons 8f having position fixing parts 49f, 49h, and 49j separable to the mold (FIG. 10). 12, 14). The method of any one of the preceding claims, The guide protrusion 46d includes a carrier disk 41d held via a snap adhesive 42 suitable for the shape of the primary piston 8d, which is used for supporting the outer ring 29d. And a clutch moving bearing 25d where the guide protrusion 46d pointing radially outward is bitten into the guide groove 47a in the case 2d to support the friction moment of the outer ring 29d. Hydraulic restraint, release device characterized by a guide projection (46d) to form a position fixing (Fig. 8). The method of claim 13, In addition to sealing, it enables the axial and radial adjustment of the outer rings 29d and 29f and is assisted by the force of the disc spring 30 so that the section of the carrier disks 41d and 41f in the vertical direction is large. A hydraulic restraining and releasing device, characterized in that it is in contact with the carrier disks 41d, 41f and a reinforcement support disk 50 arranged between the disc-shaped springs 30 of the clutch moving bearings 25d, 25f. 8, 10). The method of any one of the preceding claims, A conveyance in which the damping ring 61 fixed to the outer collar 63 of the outer ring 29l is concentric with the guide coating 6d via the spring arms 62 which are distributed around and elastically formed inward. A hydraulic, restraining and releasing device which is in contact with the section 64 of the body plate 41l (Fig. 17). The method of claim 15, An axially sealed lip member 60 in which the damping ring 61 is guided inward in the radial direction to the side where the clutch movement bearing 25l is pointed on the front side and in contact with the vertical section of the carrier disk 41l. And on the opposite side and having a section formed axially or radially complementary to the connecting contour of the inner ring 28d, which section has a maze-shaped seal or an inner ring section. Hydraulic restraint, release device characterized in that for forming a seal. The method of claim 1, One installation space 33 is formed, which extends axially in the direction of the case 2b of the inner ring 28b and of the outer ring 29b in which the installation space as a lubricant reservoir is formed and is radial. Hydraulic restraint, release device characterized in that the gap (28b). The method of claim 17, A fixed or rotating inner ring 28b or outer ring 29b is formed with a reservoir body, which ensures the supply of lubricant to the roller body 34 of the clutch movement bearing 25b. Hydraulic restraint and release device. The method of claim 17 or 18, The lubricating material can be supplied to the roller bodies 34 where the conveying grooves 35 then belong to the inner ring 28b or the outer ring 29b lying opposite from the lubricating material reservoir or reservoir body. Hydraulic restraint, release device characterized in that the transfer grooves (35). The shape ring completely fills the resulting annular clearance between the clutch moving bearing 25c and the case 2c and in the case of the released friction clutch the axial section is partly taken into the grooves of the case 2c and A hydraulic restraining and releasing device characterized by such a shaped ring (40) in which the friction matrix of the inner ring (28c) is supported in the case by a mold closed through the upper ring. The method of claim 1, The support means is attached to the secondary pistons (9g to 9j), the support means is a hydraulic restraint, release device, characterized in that to release the adjustment passage restriction or position fixing of the secondary piston (9g to 9j). The method of claim 21, One elastic stop ring 52 is inserted into the annular groove 53g in the case 2g, which is located in the peripheral groove 54g of the secondary piston 9g, where the peripheral groove ( 54g), wherein the longitudinal extension exceeds the width of the resilient retaining ring (52). The method of claim 21, An elastic stop ring is inserted into the peripheral groove of the secondary piston, which is held in the yellow groove of the case at the installation position, where its longitudinal extension extends beyond the width of the elastic stop ring. Hydraulic restraint and release mechanism featuring a piston. The method of claim 21, The elastic stop ring 52 located in the case 2j for fixing the position of the secondary piston 9 is located in the peripheral groove 54i of the secondary piston 9i suitable for the width of the elastic stop ring. Hydraulic restraint, release device (Fig. 13). The method of claim 21, The secondary piston 9h is arranged in the annular flange 5 of the guide coating 6h with its one end in the installation position, supported by the projections 55 protruding in the axial direction, and A hydraulic restraint and release device, characterized in that the other end thereof is in contact with the collar 51 of the case via a collar 16 which is inwardly radially inwardly connected (FIG. 12). The method of claim 21, A hydraulic restraining and releasing device, characterized in that the secondary piston 9j is directly re-injected as an insert part in a pressure casting operation or a plastic die casting method for manufacturing the case 2j (Fig. 14). The method of claim 26, The secondary piston has at least one peripheral groove 54j for fixing the secondary piston 9j in the axial direction, and the peripheral groove is filled as an injection material in the manufacturing process of the case 2j. Hydraulic restraint, release device. In the groove in the center of the case, a radial gap with respect to the inner wall is inserted, and guide coatings 6e to 6k are inserted in the guide coating, while the piston bridges the radial gap between the guide coating and the inner wall. Axially movably guided, wherein the piston has its one front side sealed and bound to a pressure chamber 13 formed in a circular ring shape and away from the pressure chamber 13, the other front side of the piston. The side is in contact with the clutch moving bearings 25e to 25k, where the pressure chamber 13 is surrounded by the cases 2e to 2k and the guide coatings 6e to 6k and the pressure agent via the pressure source. In the hydraulic restraint, release device for a friction clutch of a vehicle having one such case (2e to 2k) that can be filled by The pistons comprise primary pistons 8e to 8k and secondary pistons 9e to 9k, which are arranged coaxially to allow longitudinal movement with respect to one another to form a telescopic piston, wherein the case 2e to 2k And a compression spring (48e to 48k) is inserted between the clutch moving bearings (25i to 25k) fixed to the primary pistons (8e to 8k). The method of claim 28, A carrier disk 41f belongs to the primary piston 8f, and the outer ring 29f of the clutch moving bearing 25f is in contact with the carrier disk on one side, and a compression spring 48f is located on the opposite side. Hydraulic restraint, release device characterized in that the support (Fig. 10). The method of claim 29, Hydraulic carrier restraint and release device, characterized in that the carrier body plate (41f) has an attachment portion protruding in the axial direction, the spring end of the compression spring (48f) is centered on the attachment portion. The method of claim 28, The compression springs 48e to 48k are formed as conical springs whose spring ends are adapted to the friction-and / or molds in the cases 2e to 2k and the clutch moving bearings 25e to 25k to the carrier disk 41f. Hydraulic restraint, release device characterized in that the support. The method of claim 28, The case 2k, which is integral with the joining portion 68 protruding in the radial direction in the direction of the outer wall of the clutch case 56, can be supplied to the restraining and releasing device via a compression agent. Device. The method of claim 32, The joint portion 68 is provided with an exhaust connection portion 958 and a conduit connection portion 57 at their free ends, which are spaced apart in parallel and are arranged at right angles to the joint portion 68. . The method of claim 33, The junction 68 is available via two supply holes 14a and 14b which are parallel to each other, the supply holes being discharged into the conduit connection 57 and the exhaust connection 58. 69a, 69b), characterized in that the hydraulic restraint, release device. The method of claim 34, A hydraulic restraint and release device, characterized in that the supply holes (14a, 14b) are then sealed by a closed part formed as a sphere (66) each time. The method of claim 34, The supply holes 14a and 14b are conically widened at the end side and the sphere 66 is suitably supported by the mold by fastening 67 which is suitable for the mold at the time of installation in the hydraulic type. Restraint, release device. The method of claim 32, A hydraulic building and releasing device, characterized by a shifted arrangement of conduit connections 57 with respect to the scavenging connections 58. The method of claim 32, A hydraulic restraining and releasing device characterized by forming as part of the case (2k) and the joining portion (68) where the unit is made of aluminum.