WO2002004830A1 - Geberzylinder - Google Patents
Geberzylinder Download PDFInfo
- Publication number
- WO2002004830A1 WO2002004830A1 PCT/DE2001/002481 DE0102481W WO0204830A1 WO 2002004830 A1 WO2002004830 A1 WO 2002004830A1 DE 0102481 W DE0102481 W DE 0102481W WO 0204830 A1 WO0204830 A1 WO 0204830A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- master cylinder
- energy store
- pressure
- cylinder according
- master
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 27
- 230000000712 assembly Effects 0.000 claims description 8
- 238000000429 assembly Methods 0.000 claims description 8
- 230000014759 maintenance of location Effects 0.000 abstract description 2
- 238000006243 chemical reaction Methods 0.000 description 12
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 230000003993 interaction Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 210000002105 tongue Anatomy 0.000 description 2
- 230000032683 aging Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
Classifications
-
- 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
-
- 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
-
- 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
- F16D25/088—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members being distinctly separate from the axis of rotation
-
- 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
- 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
-
- 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
- F16D2025/081—Hydraulic devices that initiate movement of pistons in slave cylinders for actuating clutches, i.e. master cylinders
Definitions
- the invention relates to a master cylinder with a piston, which is driven by an actuating arm, and with an energy store, which is operatively connected to the actuating arm, the energy store also being connected to a pressure adjustment which, depending on a fluid pressure, converts the energy into the energy storage varies.
- Such master cylinders are known in a large number for the actuation of arrangements which are driven by a fluid pressure, in particular hydraulic or pneumatic arrangements. In this case, such master cylinders serve to change the pressure in the respective fluid system in order to achieve the desired effects in the fluid system.
- Such master cylinders are driven in all conceivable ways and, in addition to a motor drive, in particular also operated by human power.
- the invention relates to master cylinders that are used in motor vehicles.
- These can be master cylinders for pneumatic or hydraulic clutch systems, clutch actuations or brake systems, for example.
- Generic master cylinders are known for example from DE 198 28 198 AI or from DE 199 43 339 AI.
- These master cylinders comprise a master piston which is movable in the master cylinder driven by an actuating arm.
- a pressure can be generated in the master cylinder via the actuating arm or the master piston, which pressure can then be used in a corresponding manner. In the master cylinders shown in these publications, this pressure is used to actuate a clutch.
- reaction forces can now depend on the operating state, as described above. On the other hand, these reaction forces can also vary over longer periods. This can be caused, for example, by wear, aging, conversion processes of the fluids or losses.
- these variations are caused in particular by a friction disc wear of the clutch, which leads to an increase in pressure in the fluid system. Such an increase in pressure thus also leads to increased actuation forces which have to be applied to the actuation arm in order to disengage the clutch.
- pressure adjustments are provided in the master cylinders of DE 198 28 198 AI and DE 199 43 339 AI, which vary the energy in the energy store as a function of the fluid pressure.
- these master cylinders have additional pistons, which are operatively connected to the cylinder's hydraulic chamber via check valves.
- check valves By means of these check valves, a corresponding pressure can be maintained in a corresponding adjustment space in which the additional piston runs, so that the respective additional pistons are retained in accordance with this pressure.
- an increased energy can be stored in the corresponding spring of the energy store as a function of the fluid pressure, which energy is used to compensate for the pressure increase caused by wear.
- the pressure adjustment comprises a mechanical restraint system.
- Such a mechanical restraint system can be provided with relatively simple constructional means.
- experience has shown that mechanical measures can be reliably configured even over longer periods of time.
- hydraulic or pneumatic restraint systems on the other hand, there is a risk that leaks will occur which reduce the reliability of a pressure adjustment.
- the pressure adjustment preferably comprises an additional piston which acts on the mechanical restraint system. In this way, increased or changed pressures in the fluid system can be easily applied to the restraint system so that it can react in a corresponding manner.
- the mechanical restraint system can be implemented relatively simply and therefore inexpensively if it comprises an adjusting spring.
- Such an adjusting spring can be used to immediately follow a pressure change in the fluid system, in particular in an adjusting room, without further measures being necessary.
- the readjusting spring can thus preload a corresponding latching device in a suitable manner, so that it can easily move into a new retaining position or can be readjusted.
- the additional piston can be arranged in such a way that it relieves the mechanical restraint system as a function of the fluid pressure, and thus the adjusting spring shifts the restraint system in a corresponding manner due to the relief.
- the restraint system preferably comprises two assemblies which are displaced relative to one another or two assemblies which can be displaced against one another.
- these assemblies can be in frictional engagement or have a positive fit with one another, wherein the frictional engagement or the positive fit can be opened depending on the fluid pressure.
- the frictional engagement or the positive engagement can also be designed as a freewheel depending on the direction.
- a corresponding freewheel can be given, for example, by a locking rail into which a locking pawl has ripened.
- an adjusting spring serves to bias the latch into the latching rail.
- wedge-shaped arrangements are particularly suitable.
- wedge surfaces of rings running on one another can be provided.
- adjustment wedges or trapezoids with a wedge-shaped cross section can also be used.
- coil springs and / or disc springs can preferably be used as readjusting springs.
- spiral springs apply rotating adjustment systems, such as rings with wedge surfaces, to an adjustment voltage.
- Disc springs can, on the one hand, preferably be used to apply axial or linear forces or readjustment stresses.
- cup springs can also serve as a restraint in themselves if they are arranged bracing between two mutually displacing assemblies.
- the plate spring can also be designed as a serrated lock washer, in which case the extensions essentially have the properties of the thrust elements, while the continuous circumferential areas of such arrangements comprise plate spring characteristics.
- the master cylinder according to the invention is particularly simple if the pressure adjustment comprises an additional piston which acts on the energy store by bypassing the master piston. In this way, the compensation function of the energy store on the one hand and the pressure adjustment of the energy store on the other hand can be implemented in a structurally simple manner.
- the energy store can interact with the actuating arm via at least one plate spring.
- a plate spring has the advantage that it can be arranged around an assembly so that it can be used to act on the respective assembly from a plurality of directions. It is therefore not necessary to have separate modules for each direction Way to assemble.
- a disc spring is inherently stable due to its disc-like arrangement, so that this also makes assembly easier.
- a plate spring can be selected in a suitable manner in its spring characteristic, so that the plate spring can also be used as an energy store or in some other way, as a result of which, in addition to the simpler assembly, an active element can also be introduced.
- the assembly of the master cylinder can be simplified if the energy store interacts with the actuating arm via at least one lever which is mounted on the housing of the master cylinder outside the energy store.
- the corresponding lever can be mounted from the outside, which simplifies the assembly and in particular makes it more reliable.
- the arrangement outside is particularly advantageous if the energy store comprises a spiral spring or a spring arranged in a cylindrical space area and the lever is mounted outside this cylinder-shaped space area.
- the assembly is preferably carried out on an arm or a bearing body which is arranged on the outer housing of the master cylinder. Depending on the design requirements, the bearing arm or bearing body can protrude from the outer housing into the interior of the housing.
- the master cylinder can comprise a lever, which on the one hand has a first role with the energy store and on the other hand has a second role interacts with the actuating arm.
- Such roles are relatively expensive.
- roller arrangements are relatively reliable and low-friction, so that the overall characteristics of the master cylinder can be advantageously influenced. Since such rollers preferably run on corresponding drainage surfaces, the reaction force of the energy store can be adapted by means of relatively simple structural measures by varying the drainage surfaces.
- disk springs described above make it easier to assemble and adapt the reaction characteristics of the energy store, the bearing of the lever interacting between the energy store and the actuating arm, and the use of rollers for the interaction of the lever both with the energy store and with the actuating arm independently of one another the other features of the present invention are advantageous.
- Figure 1 shows a first master cylinder according to the invention in section, the upper region of the unactuated master cylinder with pressure adjustment adapted to low fluid pressure and the lower region to the master cylinder at high Represents fluid pressure adjusted pressure adjustment with actuated arm;
- Figure 2 is a plan view of a ramp ring of the arrangement of Figure 1;
- FIG. 3 shows a section through the ramp ring of Figure 2 along the line III-III in Figure 2;
- FIG. 4 shows a section through a support shell of the master cylinder according to FIG. 1;
- FIG. 5 shows a plan view of a plate spring for the interaction between the energy store and the actuating arm of the master cylinder according to FIG. 1;
- FIG. 6 shows a section through the plate spring according to Figure 5 along the line VI-VI in Figure 5;
- FIG. 7 shows a side view and a top view of a roller holder of the master cylinder according to FIG. 1;
- FIG. 9 shows a second master cylinder according to the invention in a similar representation as Figure 1;
- FIG. 10 shows a section through the master cylinder according to FIG. 9 along the line XX in FIG. 9;
- FIG. 11 shows an enlarged detail of the pressure adjustment of the master cylinder according to FIG. 9;
- Figure 12 is an enlargement of Figure 10
- FIG. 13 shows a detailed representation of a third master cylinder in a representation similar to that of FIGS. 1 and 9;
- FIG. 14 shows a detailed representation of a fourth master cylinder in a representation similar to that of FIGS. 1 and 9;
- FIG. 15 shows a detailed illustration of a fifth master cylinder in a representation similar to that of FIGS. 1 and 9;
- FIG. 16 shows a detailed representation of a sixth master cylinder in a representation similar to that of FIGS. 1 and 9;
- FIG. 17 shows a side view of two ramp rings of the master cylinder according to FIG. 16 and
- FIG. 18 shows a detailed representation of a seventh master cylinder in a representation similar to that of FIGS. 1 and 9.
- the in Figs. 1 to 8 master cylinder shown comprises a fluid cylinder 1, in which a master piston 2 is slidably mounted.
- the master piston 2 is located above a plastic holder 3, which is arranged in the piston is connected to an actuating arm 4 which has a retaining eyelet 5 known per se.
- the piston 2 can be displaced in the cylinder 1, as a result of which a corresponding working pressure is generated in the cylinder 1 and can be passed on to a fluid system via a connection 6.
- a contour 7 is provided on the cylinder 1. Rolls 8 roll on this contour 7, which are operatively connected to an energy store 11 via lever arms 9 (see FIG. 7) which are mounted on a holding cylinder 10.
- the energy store 11 comprises a spiral spring 12 which acts on a pressure ring 13 (see FIG. 4), against which a plate spring 14 (see FIGS. 5 and 6) bears.
- the plate spring 14 comprises a core area, which is radially circumferential and has a plate spring characteristic, and arms which act as bending beams or push rods.
- the rollers 8 are pressed onto the contour 7, so that the energy store 11 exerts a force on the contour 7 or the master piston 2 depending on the position of the actuating arm 4 and in this way a reaction force of the fluid in the cylinder 1 encountered.
- the reaction characteristic of the actuating arm 4 when the master cylinder 1 is actuated can be adapted to reaction forces which are applied by the assemblies actuated by the master cylinder 1, such as, for example, a clutch.
- the individual mounting of the rollers 8 on the levers 9 makes it easy to assemble this assembly by suspending the levers 9 in the cylinder 10. Due to the plate spring 14, which is arranged as a radially rotating assembly around the contour 7, the lever 9 and the rollers 8 are held on the contour 7 in a structurally simple manner, so that the overall arrangement can be assembled relatively easily.
- the pressure adjustment 15 of the master cylinder according to FIG. 1 comprises two ramp rings 16, 17 which are mounted in a housing 18 of the master cylinder such that they can be rotated relative to one another.
- the ramp ring 16 is supported on the housing 18 and has three ramps 19 (see FIGS. 2 and 3), while the ramp ring 17 comprises complementary ramps. It goes without saying that, depending on the specific balance of forces, other ramp shapes how more or fewer ramps can be provided. As can be seen immediately, rotation of the ramp ring 16 with respect to the ramp ring 17 can result in an axial displacement of the ramp ring 17 with respect to the housing 18.
- the pressure adjustment 15 also includes a spiral spring 21 which biases the ramp ring 16 in rotation.
- the ramp ring 17 is acted upon by the spring 12 of the energy store 11 and pressed against the ramp ring 16, so that the two ramp rings 16 and 17 are in frictional engagement with one another. In the unloaded state or when the actuating arm 4 is not actuated, the two ramp rings 16 and 17 remain stationary relative to one another due to the frictional engagement.
- the pressure adjustment also includes an adjustment space 20, which is connected to the fluid system or the interior of the cylinder 1.
- the adjustment space 20 is delimited on one side by the ramp ring 17, so that in this embodiment an increase in pressure inside the cylinder 1 lifts the ramp ring 17 from the ramp ring 16. This lifting takes place in such a way that additional energy is correspondingly stored in the energy store 11.
- this lifting causes the frictional engagement between the two ramp rings 16, 17 to be released, so that the spiral spring 21 rotates the ramp ring 16 with respect to the ramp ring 17 until the two ramps of the ramp rings 16 and 17 rest on one another again.
- the pressure in the adjusting chamber 20 is relieved of pressure, the frictional engagement between the two ramp rings 16 and 17 prevents a return movement. Rung ring 17, whereby the pressure adjustment has a permanent retention, so that correspondingly more energy is stored in the energy store 11 and is available for pressure compensation.
- the master cylinder according to FIGS. 9 to 12 has a housing 22 in which a cylinder 23 is provided, in which a piston 24 can be moved back and forth via an actuating arm 25 and which can be connected via a connection 26 to a fluid system of a motor vehicle or the like.
- the master piston 24 is sealed by means of a sealing ring 27, guided by means of a guide ring 74 and comprises a stop 28 which abuts the connector 26 when the master piston 24 is pressed in and takes the sealing ring 27 and the guide ring 74 with it when it is returned.
- the energy store 11 acts via the toggle lever 29 on the contour 7, which is operatively connected to the master piston 24 via a cylinder 30.
- the toggle levers 29 are essentially U-shaped (see FIG. 12), are mounted on the housing 22 by means of holding arms 31 at bearing points 32 and each have two rollers 33 and 34.
- the cheeks of the U's are essential for receiving the axles, while the bottom of the U's only serves for stability purposes.
- the roller 33 rolls on the contour 7, while the roller 34 sits on a disc 35 against which the spring 36 of the energy store 11 presses.
- a bearing body of the housing which surrounds the toggle levers or the bearing points 32 can also be provided. In this way, the energy store of the master cylinder according to FIGS. 9 to 12 interacts in the same way as for the master cylinder according to FIGS. 1 to 8 with the contour 7 or the master piston 24.
- levers 29 can be preassembled on the holding arms 31, so that this master cylinder can be assembled relatively reliably in the final assembly.
- This embodiment also includes a pressure compensation 15.
- This pressure compensation 15 also has an adjustment space 37, which is connected to the fluid or the interior of the cylinder 32 via a line system 38. In this way, an increase in pressure in the cylinder 23 results in an increase in pressure in the adjustment space 37.
- the embodiment according to FIGS. 9 to 12 as a restraint system 39 on a locking rail 40, in which a latch 41 engages (see in particular Fig. 11).
- the resulting detent counteracts the contact pressure of the spring 36 via a pressure disc 42 and in this embodiment is formed by circumferential grooves on a cylinder 43, in which tongues of a plate spring 44 designed as detent pawls 41 engage.
- This arrangement has the particular advantage that the restraint system does not fall back on the housing 22, as a result of which the arrangement is very compact and the housing can be made relatively light.
- the pressure in the adjustment chamber 37 acts on the restraint system via an additional piston 45. Depending on the pressure occurring in the adjustment room 37 the spring 36 is further compressed and additional energy is stored in the energy store 11.
- Figs. 13 to 18 master cylinders shown correspond essentially to the master cylinder according to FIGS. 9 to 12. They vary essentially only with regard to the additional piston used for the mechanical restraint system and with regard to the restraint system itself.
- the additional piston 46 has a conical area 47, against which a slotted trapezoidal ring 48, which acts as an adjusting wedge, nestles. This wedge braces with the housing 49 when the spring 50 presses against the additional piston 46.
- the trapezoidal ring 48 is tracked via a spring tongue 51 when the pressure increases.
- a plate spring 52 is supported between an additional piston 53 and the housing 54. Against a pressure of the spring 55, this plate spring 52 clamps between the additional piston 53 and the housing 54. On the other hand, if the pressure in the follow-up space 56 increases, the frictional engagement opens and the additional piston 53 can be displaced relative to the housing 54 towards the spring 55. If the direction of movement of the additional piston 53 changes, the spring 52 wedges again.
- FIG. 15 functions in a similar manner, with a disk spring 57 on an additional piston 58 radial in this embodiment is arranged outside the spring 59 between the additional piston 58 and a housing 73.
- disc springs with radial projections which act as bending beams or push rods, can also be used in addition, in particular to vary the rigidity.
- FIGS. 16 and 17 Similar to the embodiment according to FIGS. 1 to 8 ramp rings 60 and 61, which are arranged rotatably against one another in the housing 62. By rotating the two ramp rings 60, 61, their axial distance from one another can be varied.
- the ramp ring 60 is held in rotation by a spiral spring 63, which engages from outside through a slot 64 in the housing 62.
- the ramp rings 60, 61 are in frictional engagement.
- the pressure in the adjusting space 66 increases, this frictional engagement is released and the spiral spring 36 rotates the ramp ring 60 against the ramp of the ramp ring 61. If the pressure in the adjusting space 66 drops again, the spring 65 presses the ramp ring 61 against the ramp ring 60. whereby the frictional connection is restored and the restraint system acts restrained.
- a latching pawl 67 extends through the housing wall 68 and is pressed into a latching rail 70 of the additional piston 71 by means of a compression spring 69. This creates a form closing freewheel, which allows movement of the additional piston 71 to the spring 72, but counteracts a return movement.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2001276304A AU2001276304A1 (en) | 2000-07-07 | 2001-07-09 | Master cylinder |
DE10192652T DE10192652D2 (de) | 2000-07-07 | 2001-07-09 | Geberzylinder |
GB0300307A GB2381053B (en) | 2000-07-07 | 2001-07-09 | Master cylinder |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10032619 | 2000-07-07 | ||
DE10032619.6 | 2000-07-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002004830A1 true WO2002004830A1 (de) | 2002-01-17 |
Family
ID=7647843
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2001/002481 WO2002004830A1 (de) | 2000-07-07 | 2001-07-09 | Geberzylinder |
Country Status (5)
Country | Link |
---|---|
AU (1) | AU2001276304A1 (de) |
DE (1) | DE10192652D2 (de) |
ES (1) | ES2246676B1 (de) |
GB (1) | GB2381053B (de) |
WO (1) | WO2002004830A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2919090B1 (de) | 2014-03-14 | 2018-07-11 | Schaeffler Technologies GmbH & Co. KG | Pedalkrafterzeugungsvorrichtung |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2065250A (en) * | 1979-12-04 | 1981-06-24 | Wabco Fahrzeugbremsen Gmbh | Wear compensating arrangement in a disc brake |
EP0881134A2 (de) * | 1997-05-30 | 1998-12-02 | ABB Daimler-Benz Transportation (Technology) GmbH | Kraftspeicher |
DE19828198A1 (de) | 1998-03-13 | 1999-09-16 | Rohs Voigt Patentverwertungsge | Ausrückevorrichtung, insbesondere für eine Kupplung |
DE19943339A1 (de) | 1999-09-10 | 2001-03-15 | Rohs Voigt Patentverwertungsge | Ausrückevorrichtung, insbesondere für eine Kupplung |
-
2001
- 2001-07-09 GB GB0300307A patent/GB2381053B/en not_active Expired - Fee Related
- 2001-07-09 ES ES200350001A patent/ES2246676B1/es not_active Expired - Fee Related
- 2001-07-09 DE DE10192652T patent/DE10192652D2/de not_active Expired - Fee Related
- 2001-07-09 AU AU2001276304A patent/AU2001276304A1/en not_active Abandoned
- 2001-07-09 WO PCT/DE2001/002481 patent/WO2002004830A1/de active IP Right Grant
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2065250A (en) * | 1979-12-04 | 1981-06-24 | Wabco Fahrzeugbremsen Gmbh | Wear compensating arrangement in a disc brake |
EP0881134A2 (de) * | 1997-05-30 | 1998-12-02 | ABB Daimler-Benz Transportation (Technology) GmbH | Kraftspeicher |
DE19828198A1 (de) | 1998-03-13 | 1999-09-16 | Rohs Voigt Patentverwertungsge | Ausrückevorrichtung, insbesondere für eine Kupplung |
DE19943339A1 (de) | 1999-09-10 | 2001-03-15 | Rohs Voigt Patentverwertungsge | Ausrückevorrichtung, insbesondere für eine Kupplung |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2919090B1 (de) | 2014-03-14 | 2018-07-11 | Schaeffler Technologies GmbH & Co. KG | Pedalkrafterzeugungsvorrichtung |
EP2919090B2 (de) † | 2014-03-14 | 2022-04-20 | Schaeffler Technologies AG & Co. KG | Pedalkrafterzeugungsvorrichtung |
Also Published As
Publication number | Publication date |
---|---|
GB2381053B (en) | 2004-07-14 |
GB2381053A8 (en) | 2003-08-01 |
GB0300307D0 (en) | 2003-02-05 |
DE10192652D2 (de) | 2003-06-18 |
ES2246676B1 (es) | 2007-03-16 |
AU2001276304A1 (en) | 2002-01-21 |
GB2381053A (en) | 2003-04-23 |
ES2246676A1 (es) | 2006-02-16 |
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