GB2086477A - Wheel cylinder for a hydraulically operated drum brake - Google Patents

Wheel cylinder for a hydraulically operated drum brake Download PDF

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Publication number
GB2086477A
GB2086477A GB8131262A GB8131262A GB2086477A GB 2086477 A GB2086477 A GB 2086477A GB 8131262 A GB8131262 A GB 8131262A GB 8131262 A GB8131262 A GB 8131262A GB 2086477 A GB2086477 A GB 2086477A
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GB
United Kingdom
Prior art keywords
piston
bore
thrust bolt
axial
adjusting sleeve
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
Application number
GB8131262A
Other versions
GB2086477B (en
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deutsche Perrot Bremse GmbH
Original Assignee
Deutsche Perrot Bremse GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Deutsche Perrot Bremse GmbH filed Critical Deutsche Perrot Bremse GmbH
Publication of GB2086477A publication Critical patent/GB2086477A/en
Application granted granted Critical
Publication of GB2086477B publication Critical patent/GB2086477B/en
Expired legal-status Critical Current

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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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/22—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for pressing members apart, e.g. for drum brakes
    • 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • F16D65/546—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment for mounting within the confines of a drum brake
    • 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/561—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting within the confines of a drum brake

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

The wheel cylinder consists of a cylinder housing 1 which is supported against one brake shoe. Mounted for axial displacement in the cylinder housing is a piston 2 which can be acted upon by the pressure of a liquid. Further mounted for axial displacement in the cylinder housing is a thrust bolt 3, one end of which is supported against the piston 2 and the other end of which is supported against the other brake shoe. In order to prevent the vibrations which occur as a result of friction when the brake shoes are applied against the brake drum, it is provided that the piston is displaceable, against the force of a compression spring element 6, in the axial direction, towards the end of the thrust bolt supported against the brake shoe. The extent of this relative axial displacement is limited by stops. <IMAGE>

Description

SPECIFICATION Wheel cylinder for a hydraulically operated drum brake of a motor vehicle The invention relates to a wheel cylinder for a hydraulically operated drum brake of a motor vehicle having a cylinder housing which is supported against the one brake shoe, a piston which is mounted for axial displacement in the cylinder housing and which can be acted upon by the pressure of a liquid, and a thrust bolt which is mounted for axial displacement in the cylinder housing and one end of which is supported against the piston and the other end of which is supported against the other brake shoe.
In heavy commercial vehicles, the brakes disposed on the front axle are generally constructed as hydraulic duplex brakes whereas the brakes disposed on the rear axle are generally constructed as hydraulic simplex brakes with mechanical auxiliary actuation.
The actuation of the service brake is effected hydraulically.
It is generally known that after intiation of a braking operation when the brake shoes bear against the brake drums, so-called frictional vibrations occur.
Amplified by vibrations of the piston in the wheel cylinder, which likewise occur, these act via an unstable axle on the whole vehicle and are called "rubbing" in technical terminology.
The object of the invention is to develop the wheel cylinder of this type so that this rubbing is inhibited.
According to the invention, this problem is solved with a wheel cylinder of the type in question which is characterised in that the piston is displaceable, against the force of a compression spring element, in the axial direction, towards the end of the thrust bolt supported against the brake shoe and that the extent of this relative axial displacement is limited by stops.
As a result of the construction of the wheel cylinder according to the invention, the frictional vibrations occurring when the brake shoes are applied against the brake drums after initiatibn of a braking operation are damped, as a result of which the rubbing is prevented.
The spring rate of the compression spring element is preferably adjusted to the extent of the relative axial displacement determined by the stops in such a manner that the maximum relative axial displacement occurs at 50 percent of the maximum compressive force of the piston.
In a form of embodiment of the wheel cylinder which is particularly simple in construction from the design point of view, it is provided that the thrust bolt is made in two parts, in which case the one part has an axial bore and the the other part has an axial projection which projects into the bore and is guided in this for displacement, that the compression spring element is disposed between the two parts of the thrust bolt and that the stops are formed by the bottom of the bore in the one part of the thrust bolt and by the end face of the projection on the other part of the thrust bolt.
This design principle can be realized in a wheel cylinder with automatic adjustment, wherein the axially movable but non-rotatable thrust bolt is screwed into an axially displaceable adjusting sleeve which is supported against the piston, in such a manner that the piston has an axial bore and the adjusting sleeve has an axial projection which projects into the bore and is guided for axial displacement in this, that the compression spring element is disposed between the piston and the adjusting sleeve and that the stops are formed by annular shoulders of the adjusting sleeve and of the piston.
This design principle can also be realized, however, in such a manner that the piston is provided with an axial bore and a smaller bore following axially on this, that inserted in the smaller bore is an insert which comprises an axial projection which is adjacent to the adjusting sleeve and on which a ring is guided for axial displacement, which ring bears against the adjusting sleeve, that the ring and the end region of the adjusting sleeve are adapted for displacement in the bore of the piston, that the compression spring element is disposed between the insert and the ring and that the stops are formed by annular shoulders of the piston and of the ring.
In a further development of the invention which is advantageous from the manufacturing point of view, it is provided that the piston is provided with an axial bore, a smaller bore following axially on this and an even smaller bore following axially on this, that the thrust bolt is guided for axial displacement in the bore of the piston and comprises an axial projection which is guided for axial displacement in the smallest bore of the piston, that the compression spring element is disposed between the piston and the thrust bolt and that the stops are formed by annular shoulders of the piston and of the thrust bolt.
The spring element of the wheel cylinder preferably consists of cup springs.
The arrangement is such that when the maximum relative axial displacement determined by the stops is reached, the cup springs are not pressed locked.
Accordingly, the cup springs are not stressed to the load limit.
Some examples of embodiment of the invention are illustrated in the drawing and will be explained in more detail below.
Figure 1 shows a longitudinal section through a wheel cylinder according to a first form of embodiment, Figure 2 shows a longitudinal section through a wheel cylinder according to a second form of embodiment, Figure 3 shows a longitudinal section through a wheel cylinder according to a third form of embodiment, Figure 4 shows a longitudinal section through a wheel cylinder according to a fourth form of embodiment, and Figure 5 shows a longitudinal section through a wheel cylinder according to a fifth form of embodiment.
The wheel cylinder shown in Figure 1 is intended for a hydraulic duplex brake disposed on the front axle of a motor vehicle, particularly a heavy commercial vehicle. This wheel cylinder is provided with an automatic adjustment means to compensate for the brake wear, which is explained in more detail in the DE-PS 2003026. The wheel cylinder has a cylin der housing 1 which is supported by its right-hand end against a brake shoe (not shown). Mounted for axial displacement in the cylinder housing 1 is a piston 2, the right-hand end face of which can be acted upon by the pressure of a liquid. Further mounted for axial displacement in the cylinder housing 1 is a thrust bolt 3, the right-hand end of which bears against the left-hand end face of the piston 2 and the left-hand end of which is supported against the left hand brake shoe (not shown).The thrust bolt 3 consists of two parts 3a and 3b which are axially displaceable to a limited extent in relation to one another. Forthis purpose, the part3a ofthethrust bolt 3 bearing against the brake shoe (not shown) is provided with an axial bore 4, and the part 3b of the thrust bolt 3 bearing against the piston 2 is provided with an axial projection 5 which projects into the bore 4 and is guided in this for axial displacement.
Disposed on the axial projection 5 of the part 3b of the thrust bolt are cup springs 6 which bear against end faces 7 and 8 of the parts 3a and 3b of the thrust bolt respectively. The bottom 9 of the axial bore 4 in the part 3a of the thrust bolt and the end face 10 of the axial projection 5 of the part 3b of the thrust bolt form stops which limit the extent of the relative axial displacement of the two parts 3a and 3b of the thrust bolt 3.
When the right-hand end face of the piston 2 is acted upon by the pressure of the brake fluid, then the piston moves towards the left in the cylinder housing 1, as a result of which the thrust bolt 3 is driven out of the cylinder housing 1 and the two brake shoes are forced apart. Under the force exerted by the piston 2 and the reaction force exerted by the left-hand brake shoe, the cup springs 6 are compressed and a relative axial displacement takes place between the two parts 3a and 3b of the thrust bolt 3. With increasing loading of the thrust bolt, the projection 5 of the part 3b of the thrust bolt travels ever further into the bore 4 of the part 3a of the thrust bolt until it strikes with its end face 10 against the bottom 9 of the bore 4.When this state is reached, the braking force is no longer transmitted via the cup springs 6 but directly from the part 3b of the thrust bolt to the part 3a of the thrust bolt. The spring rate of the cup springs 6 is adapted to the extent of the relative axial displacement determined by the distance Fofthe bottom 9 of the axial bore4 of the part 3a of the thrust bolt from the end face 10 of the axial projection 5 on the part 3b of the thrust bolt in such a manner that the maximum relative axial displacement occurs at 50 percent of the maximum compressive force of the piston 2. This state then also defines the maximum compression of the cup springs 6. This arrangement is such that the cup springs 6 are not pressed locked at this maximum compression and therefore are not stressed to the load limit.
The wheel cylinder shown in Figure 2 serves for installation in a hydraulic simplex brake with mechanical auxiliary actuation, disposed on the rear axle of a motor vehicle, particularly a heavy com mercial vehicle. This wheel cylinder is likewise pro vided with an automatic adjusting means to com pensate for the brake wear. Mounted for axial dis placement in the wheel cylinder 1' is a piston 2', the right-hand end face of which can be acted upon by the pressure of a liquid. Supported against the left hand end face of the piston 2' is an adjusting sleeve 11 which is mounted for axial displacement and rotation in the cylinder housing 1'. Screwed into this adjusting sleeve 11 is a thrust bolt 3' which is connected to the associated brake shoe (not shown) being held against rotation in relation thereto.To compensate for the brake wear, the adjusting sleeve 11 is turned by means of a coarse-thread drive and a one-way coupling. Since the thrust bolt 3' is prevented from turning, the consequence is that it is screwed out of the adjusting sleeve 11. Since the construction and the mode of operation of such an automatic adjusting means is generally known, it does not need any further explanation.
As in the example of embodiment shown in Figure 1, the thrust bolt 3' is made in two parts so that the statements regarding this apply in a corresponding manner to the example of embodiment shown in Figure 2.
The wheel cylinder shown in Figure 3, which is likewise intended for installation in the hydraulic simplex brake with mechanical auxiliary actuation disposed on the rear axle of a motor vehicle, differs from the wheel cylinder shown in Figure 2 essentially in that it comprises a thrust bolt 3" in one piece.
The adjusting sleeve 11' is provided with an extension 13 at its end adjacent to the piston 2". The piston 2" is provided with an axial bore 12 in which an axial projection 14 on the extension 13 is guided for displacement. Disposed on the axial projection 14 of the extension 13 are cup springs 6" which are supported against an end face 15 of the extension 13 and an end face 16 of the piston 2". The extent of the maximum relative axial displacement of the piston 2" in relation to the thrust bolt 3 is determined by the distance F between an annular shoulder 17 disposed at the right-hand end of the adjusting sleeve 11' and an annular shoulder 18 disposed on the piston 2".
When the right-hand end face of the piston 2" is acted upon by the pressure of a liquid, then this compressive force is transmitted via the cup springs 6" to the extension 13 which is connected to the adjusting sleeve 11' and the thrust bolt 3". With increasing loading; the cup springs 6" are compressed until the annular shoulder 18 of the piston 2" comes to bear against the annular shoulder 17 of the adjusting sleeve 11'. The force exerted on the piston is then transmitted directly to the adjusting sleeve 11'. The cup springs 6" can therefore not be pressed locked and consequently cannot be stressed up to the load limit. So long as the maximum loading of the cup springs determined by the distance F is not reached, however, these have a damping effect to prevent the rubbing.
The form of embodiment according to Figure 3 has the advantage over that of Figure 2 that the easing clearance does not have to be greater by the spring travel F.
A further development of the form of embodiment according to Figure 3, which is advantageous from the manufacturing point of view, is shown in Figure 4. The piston 2" ' is provided with an axial bore 24 in which the adjusting sleeve 11" and a ring 22 bearing against this are guided for axial displacement. In addition to the bore 24, the piston 2" ' is provided with a bore 25, coaxial with this, of smaller diameter as a result of which an annular shoulder 18' is formed at the transition to the bore 24. Inserted in the bore 25 of the piston 2" ' is an insert 20 which bears against the bottom of the bore 25. The insert 20 is provided with an axial projection 21 adjacent to the thrust bolt 3" ',as a result of which an annular end face 23 is formed at the transition to the projection 21.The ring 22 is guided for axial displacement on the projection 21 of the insert 20. Disposed on the axial projection 21 are cup springs 6" 'which are supported against the end face 23 of the insert 20 and against the ring 22. The extent of the maximum relative axial displacement of the piston 2" ' in relation to the thrust bolt 3" ' is determined by the distance F between the annular shoulder 18' of the piston 2" 'and the ring 22.
When the right-hand end face of the piston 2" ' is acted upon by a pressure fluid, this compressive force is transmitted from the insert 20 via the cup springs 67 'to the ring 22 which bears against the adjusting sleeve 11". With increasing loading, the cup springs 6" 'are compressed until the annular shoulder 18' of the piston 2" 'comes to bear against the ring 22. The force of the piston 2" ' is then transmitted directly to the adjusting sleeve 11".
In Figure 5, a further development of the form of embodiment according to Figure 1 which is advantageous from the manufacturing point of view and which makes use of the principle of Figure 3 is shown. The thrust bolt 3" " is likewise made in two parts and its part 3b' is guided four displacement in an axial bore 24' of the piston 2" ".The part 3b' of the thrust bolt 3" " is provided with an axial projection 5 as a result of which an annular end face 9' is formed at the transition to the projection 5'. The piston 2" " is additionally provided with an axial bore 25' with a smaller diameter, as a result of which an annular shoulder 18" is formed at the transition to the bore 24'.The piston 2" " is further provided with a coaxial bore 26 with an even smaller diameter as a result of which an annular end face 27 is formed at the transition to the bore 25'. The axial projection 5' on the part 3b' of the thrust bolt 3" " is guided for axial displacement in the bore 26. Disposed on the axial projection 5' of the part 3b' are cup springs 6" " which are supported against the end face 27 of the piston 2" " and against the end face 9' of the part 3b'.
The extent of the maximum relative axial displacement of the piston 2" " in relation to the part 3b' of the thrust bolt 3" " is determined by the distance F between the annular shoulder 18" of the piston 2" " and the end face 9' of the part 3b' of the thrust bolt 3"".
When the right-hand end face of the piston 2" " is acted upon by the pressure of a liquid, then this compressive force is transmitted via the cup springs 6" "to the part 3b' of the thrust bolt 3" ".With increasing loading, the cup springs 6" " are compressed until the annular shoulder 18" of the piston 2" "comes to bear against the end face 9' of the part 3b' of the thrust bolt 3" ".The force of the piston 2" " is then transmitted directly to the thrust bolt 3" ".

Claims (8)

1. A wheel cylinder, for a hydraulically operated drum brake of a motor vehicle, having a cylinder housing to bear against one brake shoe, a hydraulic piston in the cylinder housing and a thrust bolt axially displaceable in the cylinder housing with an inner end bearing againstthe piston and a projecting outer end to bear against the other brake shoe, characterised thereby that the piston is axially displaceable, against a compression spring element, relatively to the thrust bolt, towards the outer end thereof, and to an extent limited by stops.
2. A wheel cylinder as claimed in claim 1, characterised in that the spring rate of the compression spring element is such that the maximum relative axial displacement of the thrust bolt up to the stops occurs at 50 percent of the maximum spring compression.
3. A wheel cylinder as claimed in claim 1 or 2, characterised in that the thrust bolt is made in two parts, one part having an axial bore and the other part having an axial projection which projects into and is guided for displacement in the bore, the compression spring element being disposed between the two parts of the thrust bolt and the stops being formed by the bottom of the bore in the one part and by the end face of the projection on the other part of the thrust bolt.
4. Awheel cylinder as claimed in claim 1 or 2 and having automatic adjustment, the thrust bolt being non-rotatable and screwed into an axially displaceable and rotatable adjusting sleeve which is supported against the piston, characterised in that the piston has an axial bore and the adjusting sleeve has an axial projection which projects into and is guided for axial displacement in the bore, the compression spring element being disposed between the piston and the adjusting sleeve and the stops being formed by annular shoulders on the adjusting sleeve and the piston respectively.
5. Awheel cylinder as claimed in claim 1 or2, and having automatic adjustment, the thrust bolt being non-rotatable and screwed into an axially displaceable and rotatable adjusting sleeve which is supported against the piston, characterised in that the piston has a first axial bore and a smaller second axial bore into which extends an insert on an axial projection from the adjusting sleeve, the projection carrying a ring guided for axial displacement thereon and bearing against the adjusting sleeve, the ring and the adjacent end of the adjusting sleeve being displaceable in the first bore of the piston, the compression spring element being disposed between the insert and the ring and the stops being formed by annular shoulders of the piston and of the ring.
6. Awheei cylinder as claimed in claim 1 or 2, characterised in that the piston is provided in series with a first axial bore, a smaller second axial bore and a smallest third axial bore, the thrust bolt being guided for axial displacement in the first bore and comprising an axial projection which is guided for axial displacement in the smallest bore, the compression spring element being disposed between the piston and the thrust bolt and the stops being formed by annular shoulders of the piston and of the thrust bolt respectively.
7. Awheel cylinder as claimed in any foregoing claim, characterised in that the spring element con sistsofa stack of cup springs.
8. A wheel cylinder substantially as described with reference to any Figure of the accompanying drawings.
GB8131262A 1980-10-17 1981-10-16 Wheel cylinder for a hydraulically operated drum brake Expired GB2086477B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE3039295A DE3039295C2 (en) 1980-10-17 1980-10-17 Wheel cylinder for a hydraulically actuated drum brake of a motor vehicle

Publications (2)

Publication Number Publication Date
GB2086477A true GB2086477A (en) 1982-05-12
GB2086477B GB2086477B (en) 1984-06-06

Family

ID=6114625

Family Applications (1)

Application Number Title Priority Date Filing Date
GB8131262A Expired GB2086477B (en) 1980-10-17 1981-10-16 Wheel cylinder for a hydraulically operated drum brake

Country Status (5)

Country Link
AT (1) AT386659B (en)
DE (1) DE3039295C2 (en)
FR (1) FR2492488B1 (en)
GB (1) GB2086477B (en)
IT (1) IT1145971B (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2281942A (en) * 1993-09-15 1995-03-22 Automotive Prod France Hydraulic actuators
FR2727164A1 (en) * 1994-11-23 1996-05-24 Fichtel & Sachs Ag CYLINDER-PISTON ASSEMBLY FOR HYDRAULIC INSTALLATIONS, IN MOTOR VEHICLES
DE102020112068A1 (en) 2020-05-05 2021-11-11 Schaeffler Technologies AG & Co. KG Piston device of a slave cylinder device and slave cylinder device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2691772B1 (en) * 1992-05-26 1994-07-22 Bendix Europ Services Tech WATERPROOF SLIDING DEVICE.

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
US2224215A (en) * 1938-08-06 1940-12-10 Samuel M Chartock Brake
DE1081788B (en) * 1956-07-07 1960-05-12 Bayerische Motoren Werke Ag Device on hydraulically operated inner shoe brakes of motor vehicles
US3035666A (en) * 1957-10-10 1962-05-22 Daimler Benz Ag Brake installation
FR1202074A (en) * 1957-10-10 1960-01-07 Daimler Benz Ag Device to compensate for the action of ovalized brake drums of shoe brakes
US3027980A (en) * 1958-09-03 1962-04-03 Gen Motors Corp Vehicle-drum brake
US3177978A (en) * 1962-04-02 1965-04-13 Chrysler Corp Brake vibration eliminator
GB1264626A (en) * 1969-01-20 1972-02-23
DE2320022C2 (en) * 1973-04-19 1981-09-17 Knorr-Bremse GmbH, 8000 München Brake cylinders for vehicles, in particular rail vehicles
JPS54108882U (en) * 1978-01-19 1979-07-31

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2281942A (en) * 1993-09-15 1995-03-22 Automotive Prod France Hydraulic actuators
GB2281942B (en) * 1993-09-15 1997-08-13 Automotive Prod France Hydraulic actuators
FR2727164A1 (en) * 1994-11-23 1996-05-24 Fichtel & Sachs Ag CYLINDER-PISTON ASSEMBLY FOR HYDRAULIC INSTALLATIONS, IN MOTOR VEHICLES
GB2295428A (en) * 1994-11-23 1996-05-29 Fichtel & Sachs Ag Hydraulic cylinder
US5704462A (en) * 1994-11-23 1998-01-06 Fichtel & Sachs Ag Cylinder for hydraulically operated clutches and brakes and hydraulically operated clutch assemblies for motor vehicles
GB2295428B (en) * 1994-11-23 1999-03-10 Fichtel & Sachs Ag Hydraulic cylinder
ES2127084A1 (en) * 1994-11-23 1999-04-01 Fichtel & Sachs Ag Cylinder for hydraulically operated clutches and brakes and hydraulically operated clutch assemblies for motor vehicles
DE102020112068A1 (en) 2020-05-05 2021-11-11 Schaeffler Technologies AG & Co. KG Piston device of a slave cylinder device and slave cylinder device
DE102020112068B4 (en) 2020-05-05 2022-03-03 Schaeffler Technologies AG & Co. KG Piston device of a slave cylinder device and slave cylinder device

Also Published As

Publication number Publication date
FR2492488B1 (en) 1989-06-02
GB2086477B (en) 1984-06-06
AT386659B (en) 1988-09-26
IT8112651A0 (en) 1981-10-15
FR2492488A1 (en) 1982-04-23
IT1145971B (en) 1986-11-12
DE3039295C2 (en) 1983-07-28
DE3039295A1 (en) 1982-05-13
ATA432281A (en) 1988-02-15

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PCNP Patent ceased through non-payment of renewal fee