GB2273541A - A hydraulic friction clutch actuator having a brake fluid and mineral oil resistant seal - Google Patents
A hydraulic friction clutch actuator having a brake fluid and mineral oil resistant seal Download PDFInfo
- Publication number
- GB2273541A GB2273541A GB9325675A GB9325675A GB2273541A GB 2273541 A GB2273541 A GB 2273541A GB 9325675 A GB9325675 A GB 9325675A GB 9325675 A GB9325675 A GB 9325675A GB 2273541 A GB2273541 A GB 2273541A
- Authority
- GB
- United Kingdom
- Prior art keywords
- annular
- disengaging
- scraper
- ring
- lips
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
- F16J15/3236—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips with at least one lip for each surface, e.g. U-cup packings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
- B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
- B60T11/16—Master control, e.g. master cylinders
- B60T11/236—Piston sealing arrangements
-
- 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
-
- 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
-
- 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
- F16D2300/00—Special features for couplings or clutches
- F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
Abstract
A hydraulic friction clutch actuator's seal 1 is manufactured from a brake fluid and mineral oil resistant material, eg polyester elastomer, and has sealing lips 2, 3 facing an annular chamber 25 formed between piston 31, having a disengaging bearing 33, and annular casing 23. The seal has a pair of scraper lips 4, 5 formed facing towards the piston 31. These scraper lips 4, 5 prevents contaminates entering the chamber 25 and seal the actuator when it is being vacuumed filled. Seal 1 may be made from two elements (7, 8 fig 2) one having the sealing lips 2, 3 the other having the scraper lips 4, 5. The sealing lip element is made of brake fluid resistant EPDM while the scraper lip element is made of mineral oil resistant NBR or HNBR and may have an integral sheet metal stiffening ring (15 fig 3). A support disc (14 fig 4) for radial guidance may be placed between the two elements of the seal. <IMAGE>
Description
Hydraulically Operated Disengaging Slave Cylinder for a Vehicle Friction Clutch
The invention rlats to a hydraulically operatea disengaging slave cylinder for a vehicle friction clutch.
A hydraulically operated disengaging device for vehicle friction clutches is known from EP-A 19 55 21. The disengaging device comprises a slave cylinder arranged concentric to an input shaft o a gear following the fiction clutch ill the drive system of the vehicle, which is connected to a master cylinder operated by the driver via a hydraulic lead. The slave cylinder has an annular casing, wnicn contains a hydraulic pressure chamber bounded radially by coaxial cylinder surfaces.An annular piston, which is arrangea radially on the inner cylinder surface with a larger diameter as well as on the outer cylinder surface with a smaller diameter, may be movea axially in tne pressure chamber, which may be rifled with a hydraulic pressure fluid for disengagement o tne clutch. The annular piston is provided with a sealing ring made of elastic material, which abuts the two cylinder surfaces wnln sealing lips to form a seal.
The usual pressure fluid used in clutch disengaging devices is the brake fluid known from vehicle brake systems. Brake fluids are usually pressure fluids manufactured on a glycol ether base, e.g. monoethers of iow polyethylene glycols.
Such pressure fluids are relatively aggressive fluids and consequently the material of the sealing ring is selected to be compatible with such brake fluids. Conventional sealing rings are usually made of ethylene propylene diene rubber (EPDM).
Disengaging slave cylinders of the aforementioned type are installed between the engine and gear concentric to the gear input shaft. This means at least traces mineral oil can reach the sealing ring from the side of the annular piston.
However, since EPDM is not resistant to mineral oii, this causes failure of the disengagIng device.
The object of the invention is to increase the resistance 0 the clutch disengaging device under the operating conditions of a vehicle.
The invention relates to a hydraulically operated disengaging slave cylinder for a vehicle friction clutch which comprises the following: an annular casing containing a cylindrical hydraulic pressure chamber bounded radially by coaxial cylinder surfaces, which may be filled with a hydraulic pressure fluid for operation; an axially movable annular piston arranged radially on the cylinder surfaces; a sealing rIng, which abuts the cylinder surfaces with peripheral sealing elements, in particular sea lips, to form a seal made of a material resistant to the pressure fluid, on an end of the annular piston facing the pressure chamber, in particular in theform of a grooved sealing ring with an annular groove moulded into its face positioned axially to te pressure chamber, and a disengaging bearing on an end of the annular piston projecting from the casing.
Wcrking from such a disengaging slave cylinder, the aforementioned aim is achieved ifl a first embodiment of the invention in that the sealing ring is made of a material which is not only resistant to the brake and pressure fluid, but Is also resistant to mineral oil based fluids, and that additionally scraper lips are formed on the sealing ring on the side facIng the annular piston, which each abut one of the cylinder surfaces o the casing. The sealing ring is preferably made of a polyester elastomer, wnicn is to brake fluids of the aforementioned type as well as to mineral oil based fluids.In tis case, te scraper lips not only prevent mineral oil from penetrating into the hydraulic cycle, but are also able to remove di## deposits on the cylinder surfaces.
According to tne first embodiment of the invention, the scraper lips are moulded onto tne seag ring to orm an integral part. owexer, G second embodiment o tne invention provides that an annular scraper element is arranged axially between the annular piston and the seaiing ring; that the scraper element has elastic scraper is, wncn eac abut one of the cylinder surfaces of the casing, and tat at east the scraper lips are made of an elastic material wnicn is resistant to mineral oil based fluids. In this embodiment, the scraper element and the sealing ring may be produced from materials each adapted to the respective object. This may be achieved relatIvely inexpensively and the resistance properties of the materials may, moreover, be optimised. Nitrile butadiene (NBR) or hydrogenated nitrile butadiene (HNBR) may be used as eiastic material for the scraper element.
When the resistance of the sealing ring to hydraulic pressure fluid as mentioned above in the two embodiments of the invention is discussed, it is the resistance to pressure fluids similar to brake fluids and in particular to glycol ether based fluids, e.g. monoethers of low polyethylene glycols, which is meant in particular. Minerai oil based fluids should be understood to include lubricants in particular, e.g. oil or grease, as well as mineral oil based fuels.
In the second embodiment of the invention, the sealing or grooved ring and the scraper element may be manufactured separately and be installed separately axially one behind the other. Separate manufacture is partIcularly simple, as only the respective material need be processed in each case.
However, both components may aiso be manufactured separately and ten joined together to form a structural unit before instalation. This is simpler to handle in particular late in the rinal assembly, and there is no risk of the two rings being incorrectly insted.
Connection may be achieved in a particularly simple manner in that one of the two parts is provided with at least one peripheral annular ring at its end region facing the other, said annular ring engaging positively into a corresponding annular ring opening in the other part. The individual components are simple to manufacture in this case and assembly of the two parts does not pose any problems.
A particularly advantageous embodiment proposes that two concentrically arranged annular rings are provided, which originate from the outside or inside diameter of one part and enclose a central area of the other part from the outside, which is provided with corresponding annular ring openings.
According to a further feature of the invention, it is proposed that the scraper element comprises a stiffening ring with moulded-on sealing lips. Inclusion of a stiffening ring in the scraper element enables the pure scraping function to be achieved by lightly biased sealing lips, since these sealing lips should only contribute as little friction as possible to the entire system and should merely have a scraping function in relation to the outside pressure.
It Is proposed to provide the stiffening ring with an approximately U-shaped cross-section, a base pointing towards the annular piston and legs pointing towards the grooved ring. This structure allows the stiffening ring to be manufactured from relatively thin-walled sheet metal ana still have a high stability of shape. The two legs may thereby be angled off in a radial direction for securing the sealing lips there.
The stiffening ring, with the exception of the base region facing the annular piston, is sprayed in an advantageous manner with the material of the sealing lips. This ensures a solid support in relation to the annular piston which is not subject to wear.
For guidance of the scraper element in relation to the grooved ring, the grooved ring is arranged to engage with a corresponding projection into the U-shaped recess in the scraper element. This ensures that the sealing lips of the scraper element are securely guided in a central position in relation to tne inside bore and the outside bore of the casing of the disengaging bearing.
A further possibility for radial guidance of the scraper element is via an additional support disc, which is arranged between the scraper element and the grooved ring and has an axial projection, which engages into the U-shaped recess in the scraper element.
The invention is explained in further detail below on the basis of severai examples.
Figure 1 shows a section through the upper half of a
sealing ring made of a uniform material, with
the disengaging slave cylinder schematically indicated;
Figure 2 shows a section through the upper half of a
sealing ring made of two different materials,
once again with the disengaging slave cylinder schematically indicated;
Figure 3 shows the upper half of a section through a
an alternative embodiment of the sealing element
from Figure 2, in which the scraper element is
provided with a stiffening ring;
Figure 4 shows the section through the upper haif of a
further alternative embodiment of the sealing
element from Figure 2, which comprises a
reinforced scraper element, a support disc and
a grooved ring.
Figure 1 shows a sealing ring 1 and its installation position - indicated by dotted lines - in a disengaging slave cylinder of a vehicle friction clutch. The slave cylinder comprises an annular casing 23 concentric to a rotary axis 21 of the friction clutch, which is not shown in further detail, or of the gear input shaft connection to the clutch, said casing 23 being provided with a pressure chamber 25 which may be filled with brake fluid, in particular glycoi ether based fluid, for disengaging the friction clutch. The pressure chamber 25 is bounded radially outwards by an inner cylinder surface 27 concentric to the rotary axis 21 and radially inwards by an outer cylinder surface 29 concentric thereto and with a smaller diameter.
An axially movable annular piston 31 engages between the cylinder surfaces 27, 29, and with a stop face 6, the grooved ring 1 abuts against the end of said annular piston located in the casing 23. The piston 31 is connected to a disengaging bearing 33 at its end projecting from the casing 23. On its side facing towards the pressure chamber 25, the grooved ring 1 has two sealing lips 2 and 3, which are separated from one another by an annular groove 3 in its face and which abut the cylinder surfaces 27, 29 forming the guide diameters and are additionally pressed onto the two guide diameters by the hydraulic medium.It must be pointed out here that Figure i shows the sealing ring 1 in its relaxed preassembly state, in which it is fiexuraiiy deformed on assembly to generate contact pressure, as is indicated in dotted lines for the sealing lip 2.
Tubular conical scraper lips 4 or 5 are formed towards the piston 31 from the material of the grooved ring 1 relating to the same guide diameters. These are supported on the guide diameters 27, 29 flexuraily stressed by a very low radiai bias, since they only have a scraping function here and are only subject to external atmospheric pressure.
Manufacture from a single material involves low manufacturing cost associated with simple assembly. At the same time, the arrangement of sealing lips 2, 3 in relation to the pressure chamber 25 and the scraper lips 4, 5 in relation to the atmosphere can provide an arrangement which is most advantageous while the pressure chamber 25 is being vacuum filled with hydraulic medium in that the scraper lips 4 and 5 act as sealing lips during this operation and no air can penetrate from the outside into the evacuated pressure chamber.
Figure 2 shows a construction, in which the sealing element is made up of a grooved ring 7 and a scraper element 8. The grooved ring 7 is made, for example, from brake fluid resistant EPDM and the scraper element 8 from mineral oii resistant NBR or HNBR. The grooved ring 7 has sealing lips 2 and 3 in relation to the guide diameter, and the scraper element 8 has scraper lips 4 or 5. The scraper element 8 is, moreover, provided with a contact surface 6 on the side opposite the pressure chamber 25, wit which It abuts the annular piston 31 when installed. Grooved ring 7 and scraper element 8 are provided as an assembly unit, since both are positively joined prior to assembly.For this purpose, the scraper element 8 has two peripheral concentric annular rings 9, which are axially spaced from the scraper lips 4 and 5, so that they can engage positively in a corresponding matching contour 10 for the annular ring in the grooved ring 7. The unit thus assembled is inserted Into the guide diameters 27, 29 and the scraper element 8 may assume a sealing function against the air using the scraper lips 4 and 5 while the pressure cnamber 25 is being vacuum filled.
The annular rings radially border a ring recess 37 between them, into which the grooved ring 7 engages for guide purposes.
Figure 3 also shows the sealing element made from two separate components, wherein the grooved ring 12 is made from EPDM, for example, and has two sealing lips 2 and 3 in relation to the guide diameters. The scraper element 11 is manufactured as a composite element, in that it comprises a stiffening ring 15 with moulded-on scraper lips 4 and 5.The stiffening ring 5 is made from sheet metal, for example, and has an approximately U-shaped cross-section, in which the base i7 of the U points in the direction of the annular piston and the two legs 18 extend essentially in axial direction from the base 17 towards the grooved ring 12, and wherein the ends may be once again angled radially outwards,
The whole stiffening ring i5 is sprayed with the material of the scraper lips 4 and 5 with the except ion of the contact surface 6 ol the base i7.The grooved ring 12 aiso points in the direction of the scraper element 11 towards a peripheral projection 16, which extends into a ring recess formed by the U shape of the scraper element 11 for radial guidance of the scraper element ii. This ensures that the scraper lips 4 and 5 lie on the guide diameters with a purposely iow bias and are exposed to as iow a radial force as possibie. When installed, the scraper element 11 abuts the annular piston with the contact surface ó of the base 17, which is free from sealing materIal, for power transmission.
in comparison to Figure 3, Figure 4 shows the arrangement of a support disc 14 between the grooved ring 13 and the scraper element ii. In this case, the support disc 14 with its projection 16 is used for radial guidance of the scraper element li, whereby the support disc 14 can additionaily assume a guidance function for the grooved ring 13 by means of a ring shoulder 39. The other reference numbers used in
Figure 4 have already been explained in detail in conjunction with Figure 3.
The scraper lips described in conjunction with Figures 1 to 4 do not serve to separate hydraulic medium and mineral oil, but act to keep dirt away from the sealing lips and from the guide diameters in the area of the path of movement of the sealing lips.
Claims (17)
1. Hydraulically operated disengaging slave cylinder for a
vehicle friction clutch; said cylinder comprising:
- an annular casing (23) containing a cylindrical hydraulic pressure chamber (25) bounded radially by
coaxial cylinder surfaces (27, 29), which may be filled
with a hydraulic pressure fluid for operation;
- an axially movable annular piston (3i) arranged
radially on the cylinder surf aces (27, 29);;
- a sealing ring (i), which abuts the cylinder surfaces
(27, 29) with peripheral sealing elements (2, 3), particular sealing lips, to form a seal made of a
material resistant to the pressure fluid, on an end of
the annular piston (3i) facing the pressure chamber
(25), in particular in the form of a grooved sealing
ring with an annular groove (35) moulded into its face
positioned axially to the pressure chamber (25), and
- a disengaging bearing (33) on an end of the annular
piston (3i) projecting from the casing (23),
characterised in that said sealing ring (1) is made of
a material which is not only resistant to the brake and
pressure fluid, but is also resistant to mineral oil
based fluids, and that additionally scraper lips (4, 5)
are formed on the sealing ring 11) on the side facing
said annular piston (31), which each abut one of the
cylinder surfaces (27, 29) of said casing (23).
2. Hydraulically operated disengaging slave cylinder for a vehicle friction clutch; said cylinder comprising:
- an annular casing (23) containing a cylindrical
hydraulic pressure chamber (25) bounded radially by
coaxial cylinder surfaces (27, 29), which may be filled
with a hydraulic pressure fluid for operation;
- an axially movable annular piston (31) arranged
radially on the cylinder surfaces (27, 29);; - a sealing ring (1), which abuts the cylinder surfaces
(27, 29) with peripheral sealing elements (2, 3), in
particular sealing lips, to form a seal made of a
material resistant to the pressure fluid, on an end of
the annular piston (31) facing the pressure chamber
(25), in particular In the form of a grooves sealing
ring with an annular groove (35) moulded ir..c its face
positioned axially to the pressure camber (25), and
- a disengaging bearing (33) on an end of the annular
piston (3::) projecting from the casing (23j, characterised in that an annular scraper element (8; li) is arranged axially between said annular piston
(31) and the sealing ring (7; 12; i3); that said
scraper element (8; 11) has elastic scraper lips (4,
5i, which each abut one of the cylinder surfaces (27,
29) of said casing (23), and that at least said scraper
lips (4, 5) are made of an elastic material which is
resistant to mineral oil based fluIds.
3. Disengaging slave cylinder according to Claim 2,
characterised in that the sealing ring (i2; i3) and the
scraper element (11) are separately manufactured
components and are arranged separately in the casing
(23) axially one behind the other.
4. Disengaging slave cylinder according to Claim 2,
characterised in that the sealing ring (7) and the
scraper element (8) are separately manufactured
components and are joined to one another to form a unit
prior to installation in the casing (23).
5. Disengaging slave cylinder according to Claim 4,
characterised in that one of the structural parts is
provided with at least one peripheral annular ring (9)
at its end region facing the other part (7), said
annular ring (9) engaging positively into a peripheral
recess (10) with a matching contour corresponding to
said annular ring (9).
6. Disengaging slave cylinder according to ClaIm 5,
characterised in that the peripheral recess (10) is
provided on a peripheral surface of the other
structural part (7).
7. Disengaging device according to Claim 6, characterlsed in that one structural part (8) has a peripheral recess
(37) axially on its side, into which the other part (7)
extends, and that one structural part (8) has two
concentrically arranged annular rings (9), of which one
engages into a recess (10) arranged on the outer
periphery of the other part and the other engages into
a recess (10) arranged on the inner periphery of the
other part (7).
8. Disengaging slave cylinder according to one of Claims 3
to 6, characterised in that one of the two structural
parts (8) has a peripheral recess (37) axially on its
side, into which the other (7) of the two parts extends
in such a way that the parts are radially guided onto
one another.
9. Disengaging slave cylinder according to one of Claims 3
to 8, characterised in that the scraper element (11)
comprises a stiffening ring (15), in particular in the
form of a metal ring, which is fixedly joined to the
material of the scraper lips (4, 5), in particular by
being moulded onto said scraper lips (4, 5).
10. Disengaging slave cylinder according to Claim 9, caracterised in that the stiffening ring (15) is
provided with an essentially U-shaped cross-section and
has an annular base (17) adjacent to the annular piston
(31), from which annular leg walls (18) project towards
the sealing ring (12; i3).
11. Disengaging slave cylinder according to ClaIm 10,
characterised in that the leg walls (18) are angled
radially away from one another in the area 0 their
edges remote from the base (17).
12. Disengaging device according to Claim 10 or 11, characterlsed In that the stiffening ring (15) is
encased In the elastic materia of the scraper lips (, 5) with the exception of the surface (6) of te base
(17) facing the annular piston (31) and provided to
support said annular piston (31).
13. Disengaging slave cylinder according to one or Claims iO to 12, characterised in that the sealing ring (11;
12) has an annular projection (16), which engages
between the leg walls (18) of the stiffening ring (15)
and fastens the scraper element (11) and the sealing
ring (12; 13) radially to one another.
14. Disengaging slave cylinder according to one of Claims
10 to 12, characterised in that an annular support disc (14) iS provided between the scraper element (11) and
the sealing ring (13), which engages between the leg
walls (18) with an annular projection (16) and radially
guides the scraper element (15) on said support disc
(14).
15. Disengaging slave cylinder according to Claim 14,
characterised in that the support disc (14) has a ring
shoulder (39), by which It Is secured to the sealing
ring (13).
16. Disengaging slave cylinder according to one of Claims 1
to i5, characterised in that the scraper lips (4, 5)
are provided in the form of approximately truncated
cone shaped tube connections, which. abut the cylinder
surfaces (27, 29) with the end adjacent to the annular
piston (31) under flexural load.
17. Hydraulically operated disengaging slave cylinder substantially
as described with reference to, and as illustrated in any one of
the Figures of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4242627 | 1992-12-17 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB9325675D0 GB9325675D0 (en) | 1994-02-16 |
| GB2273541A true GB2273541A (en) | 1994-06-22 |
| GB2273541B GB2273541B (en) | 1996-05-29 |
Family
ID=6475537
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9325675A Expired - Fee Related GB2273541B (en) | 1992-12-17 | 1993-12-15 | Hydraulically operated disengaging slave cylinder for a vehicle friction clutch |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE4339652C2 (en) |
| FR (1) | FR2699627B1 (en) |
| GB (1) | GB2273541B (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996024781A1 (en) * | 1995-02-09 | 1996-08-15 | Valeo | Hydraulically controlled release bearing for a diaphragm clutch, particularly for a motor vehicle, comprising a guide sleeve |
| GB2344393A (en) * | 1998-10-15 | 2000-06-07 | Luk Lamellen & Kupplungsbau | Hydraulically operated clutch release unit with seal carrier |
| US6092637A (en) * | 1996-07-09 | 2000-07-25 | Fichtel & Sachs Ag | Clutch with a sealing element, in particular an elastomer seal for use in annular cylinders such as in clutches |
| FR2802271A1 (en) * | 1999-12-10 | 2001-06-15 | Luk Lamellen & Kupplungsbau | Hydraulic system, in particular, for motor vehicles comprises a pressure limiting valve with a closure element which at least over a part of its axial displacement is damped by means of a damping arrangement |
| GB2382634A (en) * | 1998-10-15 | 2003-06-04 | Luk Lamellen & Kupplungsbau | Slave cylinder having a two component seal carrier |
| WO2005063542A1 (en) * | 2003-12-09 | 2005-07-14 | Gkn Driveline International Gmbh | Hydraulic system |
| CN100368684C (en) * | 2004-06-01 | 2008-02-13 | 住友橡胶工业株式会社 | Compact simplified compressor apparatus |
| CN100523568C (en) * | 2003-12-05 | 2009-08-05 | 西门子公司 | component, chamber device and transfer device having the component |
| WO2018065013A1 (en) * | 2016-10-07 | 2018-04-12 | Schaeffler Technologies AG & Co. KG | Hydrostatic actuator with a split dynamic seal portion |
| EP3556620A1 (en) * | 2018-04-16 | 2019-10-23 | WABCO Europe BVBA | Control valve for a compressed air system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19500540A1 (en) * | 1995-01-11 | 1996-07-18 | Schaeffler Waelzlager Kg | Operating system for vehicle friction coupling |
| DE19524312B4 (en) * | 1995-07-04 | 2009-04-09 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Piston for a slave cylinder of a hydraulically actuated friction clutch |
| DE19609472A1 (en) * | 1996-03-04 | 1997-09-11 | Schaeffler Waelzlager Kg | Ring piston seal for a hydraulically actuated release system |
| DE19646852A1 (en) * | 1996-11-13 | 1998-05-14 | Schaeffler Waelzlager Ohg | Hydraulic disengagement device for friction clutch of road vehicle |
| DE19724988A1 (en) * | 1997-06-13 | 1998-12-17 | Schaeffler Waelzlager Ohg | Ring piston seal |
| DE19754700A1 (en) * | 1997-12-10 | 1999-06-17 | Schaeffler Waelzlager Ohg | Vehicular brake or clutch cylinder has two-stage seal |
| DE10028672A1 (en) * | 2000-06-09 | 2001-12-13 | Fte Automotive Gmbh | Sealing element for hydraulic piston-cylinder arrangements |
| DE10349917A1 (en) * | 2003-10-25 | 2005-05-25 | Parker Hannifin Gmbh | Ring-form sealing, wiping and guiding element of piston rod of pneumatic cylinders has one-piece guide section located axially between sealing section and wiping section and with these forms solid unit of homogenous material |
| DE102004062037A1 (en) * | 2004-12-23 | 2006-07-20 | Schaeffler Kg | Phaser |
| DE102008037806A1 (en) | 2007-08-27 | 2009-03-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Sealing arrangement for a release system |
| EP2554868B2 (en) | 2011-08-05 | 2024-01-17 | Schaeffler Technologies AG & Co. KG | Clutch actuator |
| WO2015074655A1 (en) | 2013-11-19 | 2015-05-28 | Schaeffler Technologies AG & Co. KG | Piston-cylinder arrangement for a disengagement unit, in particular for a master cylinder of a hydraulic clutch actuation device |
| DE102017102802A1 (en) | 2017-02-13 | 2018-08-16 | Schaeffler Technologies AG & Co. KG | ENGINE CYLINDER WITH SEALING ELEMENT |
| IT202100012368A1 (en) * | 2021-05-13 | 2022-11-13 | Brembo Spa | Brake caliper of a disc brake disc |
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| DE3128539A1 (en) * | 1981-07-18 | 1983-02-03 | Effbe-Werk Fritz Brumme Gmbh & Co Kg, 6096 Raunheim | Rolling-hose seal for axially moving cylinder elements |
| GB2172057A (en) * | 1985-03-07 | 1986-09-10 | Automotive Products Plc | Hydraulic actuator and method of assembly thereof |
| US4821627A (en) * | 1987-06-05 | 1989-04-18 | Leigh Monstevens Keith V | Piston and cylinder assembly |
| EP0313045A2 (en) * | 1987-10-22 | 1989-04-26 | Nissan Motor Co., Ltd. | EPDM rubber seals for hydraulic cylinders |
| US5211099A (en) * | 1991-03-20 | 1993-05-18 | Fichtel & Sachs Ag | Slave cylinder for a hydraulic actuating system of a motor vehicle friction clutch |
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| US3848880A (en) * | 1972-06-09 | 1974-11-19 | Tanner Eng Co | Fluid seal |
| DE2546805C3 (en) * | 1975-10-18 | 1981-04-16 | Kaco Gmbh + Co, 7100 Heilbronn | Sealing ring for rotatable bodies, such as shafts or the like. |
| DE2757520A1 (en) * | 1977-12-23 | 1979-07-05 | Teves Gmbh Alfred | POETRY |
| US4601374A (en) * | 1982-04-22 | 1986-07-22 | Federal-Mogul Corporation | Hydraulic clutch piston and seal |
| FR2549928B1 (en) * | 1983-07-29 | 1987-12-11 | Outillage Air Comprime | DEVICE FOR GUIDING THE SEALING AND SCRAPING OF A STEM ROD |
| GB2163497B (en) * | 1984-08-22 | 1987-09-16 | Terence Peter Nicholson | Ring seals |
| US4592558A (en) * | 1984-10-17 | 1986-06-03 | Hydril Company | Spring ring and hat ring seal |
| DE3504086A1 (en) * | 1985-02-07 | 1986-08-07 | Fichtel & Sachs Ag, 8720 Schweinfurt | DOUBLE-DRIVER CYLINDER WITH TWO RELEASE BEARINGS FOR THE OPERATION OF TRACTOR DOUBLE CLUTCHES |
| SE463632B (en) * | 1987-08-14 | 1990-12-17 | Skega Ab | PNEUMATIKTAETNING |
| US4834037A (en) * | 1987-10-14 | 1989-05-30 | Dana Corporation | Unitary molded plastic valve seal |
| DE3990401C2 (en) * | 1988-04-26 | 2001-03-22 | Exedy Corp | Release mechanism for a clutch |
-
1993
- 1993-11-20 DE DE4339652A patent/DE4339652C2/en not_active Expired - Fee Related
- 1993-12-15 GB GB9325675A patent/GB2273541B/en not_active Expired - Fee Related
- 1993-12-16 FR FR9315524A patent/FR2699627B1/en not_active Expired - Fee Related
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|---|---|---|---|---|
| DE3128539A1 (en) * | 1981-07-18 | 1983-02-03 | Effbe-Werk Fritz Brumme Gmbh & Co Kg, 6096 Raunheim | Rolling-hose seal for axially moving cylinder elements |
| GB2172057A (en) * | 1985-03-07 | 1986-09-10 | Automotive Products Plc | Hydraulic actuator and method of assembly thereof |
| US4821627A (en) * | 1987-06-05 | 1989-04-18 | Leigh Monstevens Keith V | Piston and cylinder assembly |
| EP0313045A2 (en) * | 1987-10-22 | 1989-04-26 | Nissan Motor Co., Ltd. | EPDM rubber seals for hydraulic cylinders |
| US5211099A (en) * | 1991-03-20 | 1993-05-18 | Fichtel & Sachs Ag | Slave cylinder for a hydraulic actuating system of a motor vehicle friction clutch |
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| Title |
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| MACHINE DESIGN,VOL39,No 6 MARCH 1967(CLEVELAND OHIO)J N SMITH,EARL M SMOLEY,"REFERENCE ISSUE SEALS", * |
| TABLE 7 PAGE 59,TABLES 4&5 PAGES 76&78 * |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996024781A1 (en) * | 1995-02-09 | 1996-08-15 | Valeo | Hydraulically controlled release bearing for a diaphragm clutch, particularly for a motor vehicle, comprising a guide sleeve |
| US6612414B2 (en) | 1995-02-09 | 2003-09-02 | Valeo | Hydraulically controlled clutch release bearing for a diaphragm clutch, notably for a motor vehicle, having a guide sleeve |
| US6202819B1 (en) | 1995-02-09 | 2001-03-20 | Valeo | Hydraulically controlled clutch release bearing for a diaphragm clutch, notably for a motor vehicle, having a guide sleeve |
| US6092637A (en) * | 1996-07-09 | 2000-07-25 | Fichtel & Sachs Ag | Clutch with a sealing element, in particular an elastomer seal for use in annular cylinders such as in clutches |
| GB2344393B (en) * | 1998-10-15 | 2003-07-09 | Luk Lamellen & Kupplungsbau | Hydraulic release system |
| GB2382634A (en) * | 1998-10-15 | 2003-06-04 | Luk Lamellen & Kupplungsbau | Slave cylinder having a two component seal carrier |
| GB2382634B (en) * | 1998-10-15 | 2003-07-23 | Luk Lamellen & Kupplungsbau | Slave cylinder |
| GB2344393A (en) * | 1998-10-15 | 2000-06-07 | Luk Lamellen & Kupplungsbau | Hydraulically operated clutch release unit with seal carrier |
| FR2802271A1 (en) * | 1999-12-10 | 2001-06-15 | Luk Lamellen & Kupplungsbau | Hydraulic system, in particular, for motor vehicles comprises a pressure limiting valve with a closure element which at least over a part of its axial displacement is damped by means of a damping arrangement |
| CN100523568C (en) * | 2003-12-05 | 2009-08-05 | 西门子公司 | component, chamber device and transfer device having the component |
| WO2005063542A1 (en) * | 2003-12-09 | 2005-07-14 | Gkn Driveline International Gmbh | Hydraulic system |
| CN100368684C (en) * | 2004-06-01 | 2008-02-13 | 住友橡胶工业株式会社 | Compact simplified compressor apparatus |
| WO2018065013A1 (en) * | 2016-10-07 | 2018-04-12 | Schaeffler Technologies AG & Co. KG | Hydrostatic actuator with a split dynamic seal portion |
| CN109804174A (en) * | 2016-10-07 | 2019-05-24 | 舍弗勒技术股份两合公司 | With the hydrostatic actuator for being divided into two-part dynamic sealing section |
| EP3556620A1 (en) * | 2018-04-16 | 2019-10-23 | WABCO Europe BVBA | Control valve for a compressed air system |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2699627A1 (en) | 1994-06-24 |
| GB2273541B (en) | 1996-05-29 |
| GB9325675D0 (en) | 1994-02-16 |
| DE4339652C2 (en) | 2003-10-30 |
| DE4339652A1 (en) | 1994-06-23 |
| FR2699627B1 (en) | 1995-12-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 20041215 |