WO1997001716A1 - Hydraulische ausrückvorrichtung für eine reibungskupplung - Google Patents
Hydraulische ausrückvorrichtung für eine reibungskupplung Download PDFInfo
- Publication number
- WO1997001716A1 WO1997001716A1 PCT/EP1996/002086 EP9602086W WO9701716A1 WO 1997001716 A1 WO1997001716 A1 WO 1997001716A1 EP 9602086 W EP9602086 W EP 9602086W WO 9701716 A1 WO9701716 A1 WO 9701716A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- housing
- piston
- release device
- ring
- hydraulic
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
- F16D13/755—Features relating to adjustment, e.g. slack adjusters the adjusting device being located in or near the release bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/126—Details not specific to one of the before-mentioned types adjustment for wear or play
Definitions
- the invention relates to a hydraulic release device for a friction clutch according to the features of the preambles of claims 1 and 29.
- a release device of this type is known from JP 3-186 620-A.
- the structure of this disengaging device comprises a telescopic piston which is composed of two individual pistons which can be moved coaxially into one another in an end position.
- the respective hollow-cylindrical pistons have a relatively large wall thickness, which has a disadvantageous effect on the required radial installation space of the device.
- On the pressure chamber side each piston is further provided with a radially outward extension in which an annular groove is made to accommodate a seal.
- the radially inner piston bears against the inner wall of the outer piston and the outer piston bears against the bore wall of the housing.
- a further seal is provided to seal an annular gap between a guide sleeve of the housing and the inner wall of the inner piston.
- a hydraulic disengaging device constructed according to the invention is provided with a sleeve-like shaped secondary piston to form a telescopic piston, which coaxially encloses the primary piston in a touching manner.
- the primary piston is guided by its inner diameter on the guide sleeve and the secondary piston by its outer surface in the housing of the disengaging device.
- This piston arrangement advantageously enables a desired short, axial design.
- the housing which in previous designs with one-piece pistons, in addition to the guide sleeve, ensured guidance over almost the entire working stroke, has a reduced axial length, which results in a weight and cost advantage.
- the piston according to the invention further improves handling due to the reduced overall length, as a result of which the assembly can be simplified.
- a groove sealing ring according to claim 4 which is non-detachably arranged on a reinforcement, which in turn is positively snapped onto the ring piston. Vulcanization, with which the two components are combined to form a unit, is advantageous for this purpose.
- the concept of the invention also provides a groove sealing ring in which the reinforcement is partially enclosed by the sealing material and a reinforcing section emerging from the groove sealing ring is fastened to the ring piston.
- the invention according to claim 5 ensures that the primary piston has a lower displacement resistance than the secondary piston. This mode of operation is achieved due to a smaller sealing diameter of the groove sealing ring which is provided for the primary piston in comparison to the seal which is used to seal the secondary piston in the housing.
- the relatively soft sealing lips of the groove sealing ring result in less friction than the sealing ring, which is guided in the housing under prestress and is guided in the housing, for sealing the secondary piston. Due to the different displacement resistance, when the release device according to the invention is actuated, which is triggered by actuation of the clutch pedal, the primary piston is initially displaced before the secondary piston is displaced.
- the configuration of the disengaging device according to the invention according to claims 7 and 8 provides that the secondary piston forms a stop on the housing via a collar pointing radially outwards (claim 7).
- the secondary piston is provided with a radially inward-pointing collar which engages over a shoulder on the primary piston and thus forms a stroke limitation for the primary piston.
- the housing is provided with an essentially rotationally symmetrical recess in which the Clutch release bearing can be added when the friction clutch is in an engaged position.
- the embodiment of the invention according to claims 10 and 1 1 relates to the formation of the inner and outer ring of the clutch release bearing.
- the disengaging device according to the invention is provided with a non-rotatably attached inner ring to the primary piston, and a rotatably arranged outer ring of the friction clutch.
- the embodiment according to claim 1 provides a non-rotatably indirectly connected outer ring to the primary piston and a circumferential inner ring.
- a positive, releasable bearing fixation is provided between the primary piston and a bearing ring of the clutch release bearing according to claim 12. If necessary, this arrangement enables the damaged part of the hydraulic release device to be replaced without the housing and the clutch release bearing having to be replaced together in the event of damage.
- a carrier disk is provided between the non-rotatably arranged outer ring of the clutch release bearing and the primary piston, the carrier disk being fastened to the primary piston by means of a positive snap fit in order to achieve simple, inexpensive assembly.
- a reinforced support disk is provided according to claim 14, which rests over a large area on a vertical section of the bearing inner ring, supported by the force of the plate spring.
- This support disk according to the invention effectively prevents disadvantageous lubricant leakage from the clutch release bearing and also enables both axial and radial adjustability of the outer ring. These measures favor the service life of the clutch release bearing. It is expedient, according to claim 15, to use a damping ring between the outer ring and the carrier disk, which prevents a damped, ie large radial deflection of the outer ring avoiding radial movement.
- both the inner ring and the outer ring have a section facing the housing, which are spaced radially from one another, the resulting space can be designed as a lubricant depot for lubricating the rolling elements of the Clutch release bearing.
- a storage body filled with a lubricant can be inserted into the installation space, the storage body being able to be arranged both on the fixed or rotating inner ring or outer ring of the clutch release bearing for supplying lubricant to the rolling bodies.
- conveying grooves are provided for the targeted supply of the lubricant, which are each arranged on the inner ring or outer ring opposite the lubricant depot or the storage body.
- the inventive idea according to claim 20 provides to arrange a molded ring which fills an annular gap which arises between the clutch release bearing and the housing when the friction clutch is engaged and, when the friction clutch is disengaged, protrudes into corresponding recesses in the housing.
- This advantageous embodiment effectively prevents dust from entering the rotationally symmetrical recess in the housing and the clutch release bearing as well as the guidance between the primary and secondary pistons.
- the secondary piston are assigned holding means which limit the actuating travel or fix the position of the secondary piston.
- This configuration enables multiple use of the secondary piston, for example, and thus helps to reduce costs and limit the number of parts.
- an adaptation of the maximum piston stroke by limiting or fixing the secondary piston is taken into account.
- the inventive idea according to claim 22 provides that a snap ring is inserted in the housing in an annular groove, which in the installed state engages in a circumferential groove of the secondary piston, the longitudinal extent of the circumferential groove exceeding the width of the snap ring and thus a stroke limitation of the secondary piston.
- the invention provides for a snap ring positioned in the housing, which snap locks into a circumferential groove of the secondary piston which is adapted to the snap ring width.
- the claim 26 provides that in a die-casting process or Kunststoff ⁇ injection molding process for manufacturing the housing of the secondary piston is cast as an insert directly from the housing material, whereby a position fixing of the secondary piston is achieved at the same time.
- This manufacturing method advantageously eliminates the need to machine the bore for receiving the secondary piston.
- the outer surface of the secondary piston is provided with at least one circumferential groove which is filled by the casting material in the manufacturing process of the housing.
- the invention according to claim 28 provides for the arrangement of a compression spring to maintain a preload between the clutch release bearing and the clutch actuator spring.
- the construction according to the invention comprises a piston, consisting of a primary piston and a secondary piston, which are arranged coaxially longitudinally displaceable to one another and which form a telescopic piston.
- the clutch release bearing is attached to the primary piston and a compression spring is inserted between the housing and a bearing ring of the clutch release bearing.
- This construction according to the invention does not require a pre-pressure valve and thus represents a cost reduction.
- An advantageous embodiment provides, according to claim 29, a carrier disk assigned to the primary piston, on which the clutch release bearing and the pressure spring are supported on one side.
- the carrier disc is provided with an axially projecting shoulder on which a The spring end of the compression spring is under pre-tension.
- the idea of the invention provides that the attachment centers the spring end inside or outside.
- a conical spring is provided according to claim 31, which also offers security against disadvantageous buckling and consequently does not require any guidance.
- a housing for a disengaging device which is provided in one piece with a connecting piece projecting radially from the clutch housing or in the direction of an outer wall of the clutch housing.
- This nozzle which can also be referred to as a cast-on pipe, brings about a cost reduction since additional pipelines which are difficult to assemble can be dispensed with; it also reduces the number of joints to be sealed, i.e. H. the pipe screw connection directly on the housing is no longer necessary, as is the previously required alignment of the pipes during assembly.
- the connecting piece has two feed bores running parallel to one another, which correspond to tap holes made in the line connection and the vent connection.
- To achieve effective Sealing of the feed bores is provided according to claim 35 to seal these ends with a separate closure part, a ball.
- the longitudinal bore is flared at the end. After reaching an end position, a positive caulking of a wall area of the longitudinal bore is also provided, which ensures a limited radial overlap of the ball, as a result of which the ball is held in a positive manner.
- a staggered arrangement of the line connection and the ventilation connection is also provided depending on predetermined installation conditions, the flushing connection being arranged such that it assumes the statically highest installation position.
- the inventive concept comprises a one-piece design of the housing and the connecting piece.
- This unit can be produced inexpensively as a cast part, an aluminum die casting process is particularly suitable for this.
- Figure 1 in a half section a slave cylinder housing, in which a telescopic piston according to the invention in the pressurized
- FIG. 2 shows a slave cylinder housing corresponding to FIG. 1 with a different primary piston seal
- FIG. 3 shows a release device in half section with the clutch release bearing arranged on the primary piston and having a circumferential outer ring in the engaged end position;
- Figure 4 shows the release device according to Figure 3 in the disengaged position (end position);
- FIG. 5 shows a release device with a slave cylinder housing that is optimized in terms of installation space in the axial direction and in which the clutch release bearing is shown in the engaged end position;
- Figure 6 shows the disengaging device shown in Figure 5 in the disengaged position (end position);
- Figure 8 shows the release device according to Figure 7 in the disengaged position of the clutch release bearing (end position);
- FIG. 9 shows a disengaging device which provides a groove sealing ring for sealing the pressure chamber, which has a reinforcement with which the groove sealing ring is snapped onto the primary piston in a form-fitting manner;
- FIG. 10 shows the structure of a disengaging device according to the invention, in which a compression spring is used to dispense with a pre-pressure valve between the housing and a carrier disk assigned to the clutch release bearing;
- Figure 1 a stroke limitation of the secondary piston of a release device according to the invention
- FIG. 12 shows a secondary piston inserted in a fixed position between the guide sleeve and the housing
- FIG. 13 shows a snap ring inserted in the housing, which locks into a circumferential groove of the secondary piston in order to fix the position of the secondary piston
- FIG. 14 shows a secondary ring cast in a form-fitting manner
- FIG. 15 is a view of a disengaging device which is provided with a line and flushing connection which radially emerges from the housing;
- FIG. 16 shows the release device according to FIG. 15 in a sectional view along line B-B;
- FIG. 1 7 shows a release device in a longitudinal section, which represents a variant of the release device shown in FIG. 7;
- Figure 18 is a sectional view of line A-A of Figure 1 7th
- Figures 1 and 2 show the structure of a release device 1 a according to the invention, each in half section in the pressurized state.
- the disengaging device 1 a has a housing 2 a, which is attached via an end face 3 in the installed state to a gear housing not shown in FIGS. 1 and 2.
- a rotationally symmetrically designed, multiply stepped recess 4 is made centrally in the housing 2a.
- a guide sleeve 6a centered on the end face 3 via an annular flange 5 extends within the recess 4 while maintaining a radial distance from the recess 4 of the housing 2a.
- the input shaft extending within the guide sleeve 6a is not shown, which connects a friction clutch to a manual transmission.
- a primary piston 8a is guided on a lateral surface 7 of the guide sleeve 6a, the primary piston 8a being in radial contact with the guide sleeve 6a via a narrow gap.
- grooves 24 are provided on a bore wall for lubricant would be ordered.
- the primary piston 8a which has an annular cylindrical shape, is axially displaceable on the guide sleeve 6a.
- the secondary piston 9a coaxially surrounding the primary piston 8a is also inserted axially displaceably in the recess 4 of the housing 2a.
- a centering of the guide sleeve 6a is provided by a duplication 10 provided in the ring flange 5, which bears against a step 11 of the recess 4.
- the guide sleeve 6a also serves to receive a retaining ring 12 into which a shaft sealing ring (not shown) can be inserted.
- the retaining ring 12 has a stepped design and is centered in the guide sleeve 6a.
- the retaining ring 12 bears against the ring flange 5 over a vertical section.
- the primary piston 8a has on its outer surface at the end directed towards the friction clutch a driver 23 which interacts with the collar 16 of the secondary piston 9a.
- the primary piston 8a When the piston movement is reversed, the primary piston 8a in turn initially shifts until a driver 20 inserted on the outside in the primary piston 8a comes into contact with the collar 16 of the secondary piston 9a, and then both pistons are displaced to an end position at which the collar engages 18 comes to the ring flange 5.
- the different displacement resistance between the primary piston 8a and the secondary piston 9a is determined by the sealing of both pistons trigger different frictional forces, especially due to the different sealing diameters.
- the primary piston 8a is provided with a groove sealing ring 20a, the sealing lips of which bear on the guide sleeve 6a on the one hand and on the secondary piston 9a on the other hand.
- a sealing ring 21 is provided which is inserted in a circumferential groove of the housing 2a and bears against the secondary piston 9a under prestress.
- a wiper ring 22, likewise inserted in the housing 2a, is arranged axially offset from this.
- the smaller sealing diameter and the relatively soft sealing lips of the groove sealing ring 20a result in a lower displacement resistance than the seals connected to the secondary piston 9a.
- Figure 2 shows an axially longer secondary piston 8a, which is flush with an end face of the housing 2a.
- the groove sealing ring 20 is snapped onto the primary piston 8a, in contrast to the form-fitting connection in FIG. 1.
- FIG. 3 and 4 show the release device 1 b, which is supplemented by a clutch release bearing 25b.
- the clutch release bearing 25b is completely laterally inserted into the housing 2b, for which purpose this has a recess 27b which corresponds to the contour of the clutch release bearing 25b and is introduced from an end face 26.
- the clutch release bearing 25b assumes this position when the friction clutch is engaged.
- the position of the clutch release bearing 25b shown in FIG. 4 corresponds to the released friction clutch (end position), in which the clutch release bearing 25b is axially displaced from the housing 2b.
- the clutch release bearing 25b is supported on the friction clutch via the circumferentially arranged outer ring 29b.
- both the inner ring 28b and the outer ring 29b extend axially into the housing 2b, these sections 31, 32 radially spaced delimiting an installation space 33 into which lubricant for lubricating rolling elements 34 of the clutch release bearing 25b can be introduced .
- the lubricant supply can be arranged as a depot both on the inner ring 28b (see FIG. 3) and on the outer ring 29b (see FIG. 4).
- conveying grooves 35 are provided on the inner ring 28b or outer ring 29b opposite the lubricant supply, via which grooves the lubricant can be supplied to the rolling elements 34.
- a sheet metal sleeve 36 is attached to the outer ring 29b in a form-fitting manner, on the end of which a lip seal 37 abutting the inner ring 28b is vulcanized.
- a seal 39 fastened to the holding plate 38, which rests with sealing lips on a vertical section of the outer ring 29b facing away from the contact side of the friction clutch.
- the release device 1 c shown in FIGS. 5 and 6 is largely comparable to the release device 1 b (FIGS. 3 and 4).
- an enlarged installation space is provided between the inner ring 28c and the outer ring 29c of the clutch release bearing 25c.
- a form ring 40 is fastened to the inner ring 28c, which prevents the inner ring 28c from rotating with one another due to the bearing friction torque by positive engagement of the guide cam 46c in a guide groove 47c.
- the shaped ring 40 C has a design that adapts to the contour of the recess 27c and when the rice is disengaged Exercise clutch (end position) partially engages in an opening 45 of the housing 2c.
- the release device 1 d in FIGS. 7 and 8 is provided with a clutch release bearing 25d, the inner ring 28d of which rotates.
- the structure also shows an outer ring 29d, which is supported on a carrier disk 41d.
- the carrier disk 41d which is provided with a double cross-section or in the region of the feed bore of the housing 2d with a double, is held in a rotationally fixed manner on the primary piston 8d by means of a snap 42.
- the carrier disk 41d On the outside, the carrier disk 41d has a right-angled bend to form a guide cam 46d which engages in a guide groove 47d of the housing 2d and thus prevents the outer ring 29d from rotating.
- an angular plate 43 is attached in a rotationally fixed manner, which with its long radial leg, supported by the force of the plate spring 30, rests non-positively on the carrier disk 41d and which enables a radial and axial adjustment of the outer ring 29d.
- the lip seal 37 is used, which bears against the circumferential inner ring 28d and is held by means of the sheet metal sleeve 36, which is positively attached to the outer ring 29d.
- the disengaging device 1 e shows a groove sealing ring 20e for sealing the pressure chamber 13, which forms a unit with a reinforcement 20f.
- Vulcanization which creates a permanent, non-detachable connection, is suitable for connecting the two components.
- the reinforcement 20f encloses the end area of the primary piston 8e facing the pressure chamber 13 and encloses an end area of the annular piston 8e with a cylindrical section.
- the reinforcement 20f has a radially inwardly directed snap lug 20g, which latches into an annular groove 20h of the primary piston 8e in order to achieve a positive locking.
- the reinforcement 20f formed from sheet metal by a deep-drawing process is further provided with a shoulder 17, which forms a stop 15 with the collar 16 arranged radially inward at the end on the secondary piston 9e and thus a stroke limitation of the primary piston 8e.
- a compression spring 48e which is inserted between the housing 2e and the inner ring 28e, with which a preload can be maintained between the clutch release bearing 25e and the plate spring 30 and which makes it possible to dispense with a pre-pressure valve.
- the compression spring 48e is designed as a conical spring, which offers security against buckling and also ensures a short block length.
- FIG. 10 shows a clutch release bearing 25f detachably arranged on the primary piston 8f.
- the primary piston 8f is provided on the end face with a bearing fixation 49f, on which a carrier disk 41f is detachably snapped.
- the compression spring 48f is supported on the carrier disk 41f on the housing side and the outer ring 29f of the clutch release bearing 25f on the opposite side.
- a support disk 50 is provided which, with a long leg, bears against a vertical section of the carrier disk 41f, supported by the force of the plate spring 30.
- a short leg arranged at right angles to the long leg of the support disk rests on the inside with a seal 50a on the outer ring 29f.
- FIG. 11 shows the disengaging device 1g, which is provided with a stroke limitation of the secondary piston 9g.
- an annular groove 53g is made in the housing 2g for receiving a snap ring 52.
- the snap ring 52 engages in a circumferential groove 54g which is introduced into the lateral surface of the secondary piston 9g and whose longitudinal extension exceeds the width of the snap ring by a multiple.
- the difference between the snap ring width and the longitudinal extent of the circumferential groove 54g determines the stroke of the secondary piston 9g.
- FIG. 12 shows a fixed-position secondary piston 9h, which is supported at one end on the ring flange 5 of the guide sleeve 6h and bears at its other end on a housing collar 51.
- the ring flange 5 is the Guide sleeve 6h provided with a plurality of circumferentially distributed projections 55 on which the secondary piston 9h is supported.
- the disengaging device 1 i shows a secondary piston 8i which is positioned by means of a snap ring 52 and which engages in an annular groove 53i, introduced in the housing 2i, in the installed position of the secondary piston 8i, in a circumferential groove 54i adapted to the width of the snap ring 52.
- the disengaging device 1 i is also provided with an anti-rotation device for the inner ring 28i, which is provided on the housing side with a molded ring 40i which is angled on the outside to form a guide cam 46i which engages in a guide groove 47i of the housing 2i.
- a further alternative position fixing of a secondary piston can be found in the disengaging device 1 j according to FIG. 14.
- the secondary piston 9j is designed as an insert, i. H. in the production process of the housing 2j by means of a die-casting process or plastic injection molding process, the cylindrically shaped secondary piston 9j is directly surrounded by the material of the housing 2j.
- the lateral surface of the secondary piston 9j has two parallel grooves 54j which are spaced apart and which are filled by the material of the housing 2j during the manufacturing process.
- the disengaging device 1 k which has a nozzle 68 radially emerging from the housing 2 k.
- the end piece is provided at the end with two parallel spaced connections, a line connection 57 and a vent connection 58, which are arranged at right angles to the connection piece 68.
- the line connection 57 and the ventilation connection 58 are guided through an opening 59 of the clutch housing 56 and thus allow access to the outside of the clutch housing 56.
- the vent connection 58 or flushing connection is arranged so that it is in the installed state above the line connection 57, ie at the statically highest point of the hydraulic system, which ensures that the air trapped in the hydraulic system can be effectively vented if necessary.
- the connecting piece 68 is further provided with two axially spaced feed bores 14a, 14b, which correspond to branch bores 69a, 69b, which are made in the line connection 57 and in the ventilation connection 58, respectively.
- these are at the end, d. H. effectively sealed with a ball 66 above an opening of the tap holes 69a, 69b.
- the ball 66 is held in a form-fitting manner by a caulking 67 provided radially in the direction of the center of the bore of the feed bore 14a, 14b.
- the feed bore 14a, 14b is flared at the end.
- FIGS. 17 and 18 show the disengaging device 11, which is comparable in terms of the structure of the disengaging device 1 d according to FIGS. 7 and 8.
- An outer ring collar 63 of the outer ring 29I is supported on the carrier disk 41 1, which is positively connected to the primary piston 8 d by means of a snap 42, almost on the outer circumference on a vertical section.
- a damping ring 61 is used, which is arranged between a section 64 arranged coaxially to the guide sleeve 6d, the carrier disk 41 1 and an inner wall of the outer ring collar 63.
- the damping ring 61 is centered on the inside on the section 64 via circumferentially distributed, elastically designed spring arms 62. This design of the damping ring 61 causes a damped radial deflection of the outer ring 29I toward the carrier disk 41 1.
- the damping ring 61 which is made in particular of a plastic material, is further provided on the end face facing the clutch release bearing 25l with an axial sealing lip 60 which has a radially inward, ie to the guide sleeve 6d forming shoulder that sealingly rests under prestress on a vertical section of the carrier disk 411.
- FIG. 18 shows the inclined arrangement of the spring arms 62 in the installed state of the damping ring 61, which ensures that the spring arms 62 are biased against the carrier disk 411.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19680489T DE19680489B4 (de) | 1995-06-24 | 1996-05-15 | Hydraulische Ausrückvorrichtung für eine Reibungskupplung |
BR9609315A BR9609315A (pt) | 1995-06-24 | 1996-05-15 | Dispositivo hidráulico de debreagem para embreagem de fricção |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19523011.6 | 1995-06-24 | ||
DE19523011A DE19523011A1 (de) | 1995-06-24 | 1995-06-24 | Hydraulische Ausrückvorrichtung für eine Reibungskupplung |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997001716A1 true WO1997001716A1 (de) | 1997-01-16 |
Family
ID=7765179
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1996/002086 WO1997001716A1 (de) | 1995-06-24 | 1996-05-15 | Hydraulische ausrückvorrichtung für eine reibungskupplung |
Country Status (4)
Country | Link |
---|---|
KR (1) | KR100419704B1 (de) |
BR (1) | BR9609315A (de) |
DE (2) | DE19523011A1 (de) |
WO (1) | WO1997001716A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19716473A1 (de) * | 1997-04-19 | 1998-10-29 | Fte Automotive Gmbh | Zentralausrücker für eine hydraulische Kupplungsbetätigung |
DE19746538A1 (de) * | 1997-10-22 | 1999-04-29 | Schaeffler Waelzlager Ohg | Vorlastfeder für ein Ausrücksystem einer Fahrzeugkupplung |
DE19754176A1 (de) * | 1997-12-06 | 1999-06-10 | Schaeffler Waelzlager Ohg | Führungsflächen in einem Nehmerzylinder, die durch Kugelstrahlen behandelt sind |
DE10349173A1 (de) * | 2003-10-22 | 2005-05-19 | Zf Friedrichshafen Ag | Betätigungseinrichtung für eine Kupplung |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB9606971D0 (en) * | 1996-04-02 | 1996-06-05 | Automotive Prod France | Hydraulic actuators |
FR2772443B1 (fr) * | 1997-12-11 | 2001-09-28 | Valeo | Recepteur hydraulique de commande d'embrayage notamment pour vehicule automobile |
DE19714844A1 (de) | 1997-04-10 | 1998-10-15 | Mannesmann Sachs Ag | Nutring zur Abdichtung von Zylinderflächen |
DE19716217A1 (de) * | 1997-04-18 | 1998-10-22 | Schaeffler Waelzlager Ohg | Am Ringkolben lösbar befestigtes Kupplungsausrücklager |
DE19746537A1 (de) * | 1997-10-22 | 1999-04-29 | Schaeffler Waelzlager Ohg | Nehmerzylinder mit einem aus Kunststoff hergestellten Adapter |
FR2772444B1 (fr) * | 1997-12-11 | 2000-06-16 | Valeo | Recepteur hydraulique pour commande d'embrayage, notamment pour vehicule automobile |
DE19755496B4 (de) * | 1997-12-13 | 2006-10-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Abstützring für die Vorlastfeder eines Nehmerzylinders |
DE19808315A1 (de) * | 1998-02-27 | 1999-09-02 | Schaeffler Waelzlager Ohg | Nehmerzylinder mit einem Druckstutzen, an den ein Adapter anschließbar ist, der durch eine Öffnung des Kupplungsgehäuses einführbar ist |
FR2780121B1 (fr) | 1998-06-19 | 2000-08-18 | Valeo | Dispositif de debrayage a commande hydraulique dotee d'un tube de guidage et procede d'obtention d'un tel tube |
FR2780467B1 (fr) * | 1998-06-30 | 2000-09-22 | Valeo | Recepteur hydraulique, notamment d'embrayage, a element de manoeuvre en trois pieces |
EP0984185B1 (de) * | 1998-09-02 | 2006-01-11 | FTE automotive GmbH | Hydraulische Stellvorrichtung zur Betätigung einer Kupplung, insbesondere für Kraftfahrzeuge |
FR2794507B1 (fr) * | 1999-06-04 | 2001-07-13 | Valeo | Piston et dispositif de commande hydraulique d'un embrayage de vehicule automobile comportant un tel piston |
DE10107876A1 (de) * | 2001-02-20 | 2002-08-22 | Daimler Chrysler Ag | Hydraulische Ausrückvorrichtung für eine Kupplung |
DE102004032082B4 (de) * | 2003-10-22 | 2014-01-23 | Zf Friedrichshafen Ag | Betätigungseinrichtung für eine Kupplung |
DE10349174A1 (de) * | 2003-10-22 | 2005-05-19 | Zf Friedrichshafen Ag | Betätigungseinrichtung für eine Kupplung |
DE102005053408B4 (de) * | 2004-11-19 | 2020-10-08 | Zf Friedrichshafen Ag | Betätigungseinrichtung |
DE102007019498B4 (de) | 2006-05-17 | 2020-07-02 | Schaeffler Technologies AG & Co. KG | Nehmerzylinder sowie Hydraulisches System |
EP1857699B2 (de) † | 2006-05-17 | 2020-04-15 | Schaeffler Technologies AG & Co. KG | Nehmerzylinder und Hydraulisches System |
DE102009034812B4 (de) * | 2008-08-11 | 2019-02-14 | Schaeffler Technologies AG & Co. KG | Ausrückvorrichtung für eine Reibungskupplung mit einem von einer Vorlastfeder beaufschlagten Ausrücklager |
DE102009053486B4 (de) | 2008-12-22 | 2019-06-06 | Schaeffler Technologies AG & Co. KG | Kupplungsausrücksystem für eine Reibungskupplung |
DE102016221555B3 (de) * | 2016-11-03 | 2018-01-18 | Schaeffler Technologies AG & Co. KG | Nehmerzylinder mit Dämpfer zwischen Lagerring und Stützring der Vorspannfeder |
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GB2109504A (en) * | 1981-11-12 | 1983-06-02 | Skf Kugellagerfabriken Gmbh | Removing oil and dust from piston cylinder assembly |
EP0095841A2 (de) * | 1982-05-28 | 1983-12-07 | Automotive Products Public Limited Company | Kupplungsbetätigungsanordnung für Kraftwagengetriebe |
DE4001607A1 (de) * | 1989-01-27 | 1990-08-02 | Ina Bearing Co | Kupplungs-ausrueckapparat |
DE9011432U1 (de) * | 1990-08-06 | 1990-10-11 | Fag Kugelfischer Georg Schaefer Kgaa, 8720 Schweinfurt, De | |
JPH03186620A (ja) * | 1989-12-14 | 1991-08-14 | Nachi Fujikoshi Corp | 油圧作動型クラッチレリーズ軸受装置 |
DE9313557U1 (de) * | 1993-09-08 | 1993-10-28 | Schaeffler Waelzlager Kg | Ausrückvorrichtung für eine Reibungsklupplung |
GB2287295A (en) * | 1994-03-09 | 1995-09-13 | Fichtel & Sachs Ag | An adjustable clutch actuator with a restraining device that allows for clutch wear |
DE4412927A1 (de) * | 1994-04-15 | 1995-10-19 | Schaeffler Waelzlager Kg | Hydraulisch betätigbare Vorrichtung zum Ausrücken einer Schalttrennkupplung eines Kraftfahrzeugs |
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DE4129370C2 (de) * | 1991-09-04 | 2001-11-22 | Mannesmann Sachs Ag | Hydraulisch betätigbarer Ausrücker mit Stützring und Stützschulter |
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1995
- 1995-06-24 DE DE19523011A patent/DE19523011A1/de not_active Withdrawn
-
1996
- 1996-05-15 KR KR1019970709600A patent/KR100419704B1/ko not_active IP Right Cessation
- 1996-05-15 BR BR9609315A patent/BR9609315A/pt not_active IP Right Cessation
- 1996-05-15 WO PCT/EP1996/002086 patent/WO1997001716A1/de active IP Right Grant
- 1996-05-15 DE DE19680489T patent/DE19680489B4/de not_active Expired - Fee Related
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GB2109504A (en) * | 1981-11-12 | 1983-06-02 | Skf Kugellagerfabriken Gmbh | Removing oil and dust from piston cylinder assembly |
EP0095841A2 (de) * | 1982-05-28 | 1983-12-07 | Automotive Products Public Limited Company | Kupplungsbetätigungsanordnung für Kraftwagengetriebe |
DE4001607A1 (de) * | 1989-01-27 | 1990-08-02 | Ina Bearing Co | Kupplungs-ausrueckapparat |
JPH03186620A (ja) * | 1989-12-14 | 1991-08-14 | Nachi Fujikoshi Corp | 油圧作動型クラッチレリーズ軸受装置 |
DE9011432U1 (de) * | 1990-08-06 | 1990-10-11 | Fag Kugelfischer Georg Schaefer Kgaa, 8720 Schweinfurt, De | |
DE9313557U1 (de) * | 1993-09-08 | 1993-10-28 | Schaeffler Waelzlager Kg | Ausrückvorrichtung für eine Reibungsklupplung |
GB2287295A (en) * | 1994-03-09 | 1995-09-13 | Fichtel & Sachs Ag | An adjustable clutch actuator with a restraining device that allows for clutch wear |
DE4412927A1 (de) * | 1994-04-15 | 1995-10-19 | Schaeffler Waelzlager Kg | Hydraulisch betätigbare Vorrichtung zum Ausrücken einer Schalttrennkupplung eines Kraftfahrzeugs |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19716473A1 (de) * | 1997-04-19 | 1998-10-29 | Fte Automotive Gmbh | Zentralausrücker für eine hydraulische Kupplungsbetätigung |
DE19716473C2 (de) * | 1997-04-19 | 2002-07-04 | Fte Automotive Gmbh | Zentralausrücker für eine hydraulische Kupplungsbetätigung |
DE19746538A1 (de) * | 1997-10-22 | 1999-04-29 | Schaeffler Waelzlager Ohg | Vorlastfeder für ein Ausrücksystem einer Fahrzeugkupplung |
DE19754176A1 (de) * | 1997-12-06 | 1999-06-10 | Schaeffler Waelzlager Ohg | Führungsflächen in einem Nehmerzylinder, die durch Kugelstrahlen behandelt sind |
DE19754176B4 (de) * | 1997-12-06 | 2006-07-06 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Führungsflächen in einem Nehmerzylinder, die durch Kugelstrahlen behandelt sind |
DE10349173A1 (de) * | 2003-10-22 | 2005-05-19 | Zf Friedrichshafen Ag | Betätigungseinrichtung für eine Kupplung |
Also Published As
Publication number | Publication date |
---|---|
DE19523011A1 (de) | 1997-01-02 |
DE19680489D2 (de) | 1998-11-26 |
KR19990028286A (ko) | 1999-04-15 |
BR9609315A (pt) | 1999-07-06 |
KR100419704B1 (ko) | 2004-10-22 |
DE19680489B4 (de) | 2006-05-24 |
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