EP1409319A1 - Maitre-cylindre de frein a pistons plongeurs aspirants et gorges radiales integrees dans le carter pour recevoir les joints d'etancheite - Google Patents

Maitre-cylindre de frein a pistons plongeurs aspirants et gorges radiales integrees dans le carter pour recevoir les joints d'etancheite

Info

Publication number
EP1409319A1
EP1409319A1 EP01960530A EP01960530A EP1409319A1 EP 1409319 A1 EP1409319 A1 EP 1409319A1 EP 01960530 A EP01960530 A EP 01960530A EP 01960530 A EP01960530 A EP 01960530A EP 1409319 A1 EP1409319 A1 EP 1409319A1
Authority
EP
European Patent Office
Prior art keywords
chamber
housing
master cylinder
container
annular groove
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.)
Withdrawn
Application number
EP01960530A
Other languages
German (de)
English (en)
Inventor
Hans-Jörg Feigel
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.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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
Priority claimed from DE10120913A external-priority patent/DE10120913A1/de
Application filed by Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP1409319A1 publication Critical patent/EP1409319A1/fr
Withdrawn legal-status Critical Current

Links

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
    • B60T11/20—Tandem, side-by-side, or other multiple master cylinder units

Definitions

  • the invention relates to a master cylinder, preferably a tandem master cylinder, as is required in hydraulic brake systems.
  • Master cylinders of this type serve as transmitters for actuating the pistons in the brake calipers, the pedal force exerted by the driver possibly being evenly distributed over the transmitter to the brake calipers by a brake booster.
  • a brake booster Such an encoder is described, for example, in US Pat. No. 5,187,934.
  • the cylinders were previously regularly closed at the end in the direction of actuation by a cover, while a sealing ring was screwed or caulked in at the opposite (driver-side) end, which is used to guide the push rod facing the driver and as a system serves for the secondary piston.
  • the known master cylinders with plungers have a number of disadvantages. Since several parts have to be joined together in the axial direction, the diameter of the known master cylinder is considerable. Furthermore, a large number of components are required to provide the necessary contact surfaces for the sealing sleeves.
  • the invention is therefore based on a tandem master cylinder of the type resulting from the preamble of claim 1.
  • the object of the invention is to provide a novel master cylinder of this type, which is characterized by the use of very few components and a very inexpensive structure.
  • the object is achieved by the combination of features resulting from the characterizing part of claim 1.
  • the invention therefore consists in accommodating the primary seal in a circumferential groove which is introduced directly into the housing.
  • the main advantage is that the primary seal, which is exposed to considerable forces, can be supported directly on the housing. This means that the forces do not have to be absorbed by assemblies screwed or caulked to the housing that have to be inserted into the housing. This significantly reduces the diameter of the housing with the same force absorption by the master cylinder.
  • screwing or caulking eliminates the necessary joints between components that are susceptible to faults under permanent load.
  • the preparation of the necessary ring groove within the housing is not a considerable difficulty for an automatic milling machine. With suitable devices, it is still possible to insert the ring-shaped seal into the ring groove produced in this way without any problems.
  • the use of the combination of features according to claim 2 is recommended. If a first annular groove for the primary seal is produced with the aid of the milling tool mentioned, this tool can also be used to produce an axially sets arranged second annular groove can be used, in which the annular secondary seal can then be inserted. In this way, the advantage obtained by the combination of features according to FIG. 1 increases considerably. It should also be noted that by saving the components used to support the sealing sleeves, the overall length for the master cylinder is also saved, so that it can not only be smaller in diameter but also shorter in length with the same performance.
  • the application of the inventive principle to the second secondary seal which seals the surroundings of the master cylinder from the second chamber and the expansion tank, has the further advantage that no special closure part has to be inserted at this end of the master cylinder, which in addition increases the diameter of the Master cylinder must lead.
  • the housing and its seal thus simultaneously serve to support the driver's second piston of the tandem master cylinder.
  • the second primary seal is additionally introduced into an annular groove inserted into the housing of the master cylinder. All four ring grooves can then be made with the same tool. The same also applies to the devices which serve to insert the ring-shaped seals into the associated ring grooves.
  • the material of the housing also limits a possible tilting movement of the second piston projecting into the housing.
  • a further additional simplification of the master cylinder according to the invention can be achieved by using the features according to claim 5.
  • the end of the master cylinder lying in the actuation direction is through the housing even closed in one piece. In other words, no additional cover is required which closes the master cylinder on the actuating end and thus forms the first chamber in connection with the first piston.
  • the combination of features according to claim 6 is recommended in a development of the invention.
  • the ring groove in question is inserted so deeply into the housing that the primary seals which are subjected to considerable pressure are supported by their seals which support the bottom of the groove Can support the load on the side of the groove. In this way it is safely prevented that the foot can be pulled out of the groove under pressure.
  • the springs do not act directly on the pistons, but via a preferably plate-like component which transmits the captive force applied by the spring to the piston.
  • a development of the invention according to features 11 and 12 proposes, on the one hand, to establish the flow connection between the chambers and the container chambers exclusively via flow passages in the piston and in the housing. len.
  • a collecting ring groove be provided between the primary seal and the secondary seal at least in the second chamber and that the collecting ring chamber of the first and / or second chamber be connected to the associated expansion tank through a bore.
  • a transverse bore can be provided which runs parallel to the cylinder space and which is connected to the second chamber by a tap hole. The transverse bore then leads to an expansion tank assigned to the second chamber.
  • Fig. 1 is provided with a plunger master cylinder according to the prior art
  • FIG. 2 is a sectional view of a first embodiment for a tandem master cylinder according to the invention
  • Fig. 3 shows a cross section through the master cylinder according to Fig. 2 and
  • Fig. 4 shows a second embodiment of a tandem master cylinder according to the present invention.
  • the tandem master cylinder shown in FIG. 1 is intended to explain the state of the art and has already been sufficiently described in DE-OS 19527955. Therefore, only the essential features are discussed at this point in order to make the features of the present invention clearer compared to the prior art.
  • the tandem Master cylinder 20 according to FIG. 1 has a housing 15 which is closed with a cover 48. In the housing 15, two plunger pistons 1 and 3 are guided, each of which is sealed with a primary seal 6 or 7 and a secondary seal 12 or 14 against the adjacent rooms.
  • the pistons delimit a first chamber 2 or second chamber 4.
  • a return spring 32 or 33 also acts on the pistons, the return spring 33 being bound by elements 35, 36.
  • several assemblies are inserted into the interior of the housing 21, which form the contact surfaces for the seals.
  • FIG. 2 shows a first exemplary embodiment in connection with FIG. 3.
  • identical components in connection with FIGS. 2 to 3 are not explained again insofar as they have already been described in connection with FIG. 1 .
  • the cover 48 according to FIG. 1 has been dispensed with. Rather, this cover is connected in one piece to the housing 15.
  • the housing 15 represents a reworked casting, the undercuts mainly having to be produced by appropriate milling processes.
  • the construction according to FIG. 2 has the advantage that the seals can be supported against the inner end surfaces (see, for example, inner end surface 30). End faces are integrally connected to the housing and can absorb correspondingly high forces.
  • 1 is also a circumferential collecting ring groove 45 or 46, which is inserted between the ring grooves 1, 17 and 18, 19 in the housing.
  • Bores extend from the collecting ring grooves 45, 46, a direct bore 41 and a tap hole 43 being provided, via which the first chamber 2 and the second chamber 4 are connected to the associated container chambers 5 and 10 (see FIG. 3) ,
  • the tap hole 43 opens in FIG. 2 into a transverse bore 44, which in turn opens into the second container chamber 10 (see FIG. 3).
  • the flow passages 40 and 42 through which it is possible that the chambers 2 and 4 extend into the pistons 1 and 2, are also advantageous for the design of the master cylinder according to FIG. 2, whereby the chambers are enlarged with the same external dimensions become.
  • the flow passages 40, 42 provide ventilation of the chamber when the pistons are retracted to the right in the figure.
  • the width of the circumferential annular grooves is somewhat larger than the width of the seals inserted into them. This makes it possible for pressure medium to easily get to the base of the individual seals, as a result of which the seals are guided in moisture and cannot adhere dry to the bottoms of the grooves in the housing.
  • An advantageous feature of the master cylinder according to the invention are also the recesses 28, 29, which on both sides of the ring grooves 16, 17 into the associated cam mern are inserted into the housing. These recesses, which are provided at least in the upper region of the chambers, enable or at least improve self-venting in the direction of the wheel outlets for both chambers. It is also advantageous that the recess 29 in front of the primary seal has a flow connection 60 to the annular groove of the primary seal 16, which enables self-ventilation in the direction of the wheel outlets and at the same time prevents the seals from running dry.
  • the structure of the master cylinder according to FIG. 2 is further characterized in that the two container chambers 5 and 10 are arranged next to one another transversely to the longitudinal axis of the cylinder. This saves installation space in relation to the engine compartment, since, as can be seen from FIG. 2, the master cylinder can be inserted much more deeply into the bulkhead 27 than in the structure according to FIG. 1.
  • the return springs can also be advantageously configured in FIG. 2 in accordance with the structure according to FIG. 1.
  • a construction is preferably chosen for the bondage, as is shown in connection with spring 33 in FIG. 1.
  • two spring plates 36, 37 are connected to one another via a bolt 35, the maximum distance between the two plates being fixed to one another by projections on the bolt.
  • At least one of the two spring plates 37 can slide on the bolt, so that the two spring plates 36, 37 can be moved towards one another against the force of the spring 33.
  • the spring plates are supported directly on the piston and can be locked with them or connected in any other suitable way.
  • a further simplification for a tandem master cylinder is the structure according to FIG. 4 compared to the structure according to FIG.
  • a simplification can also be achieved with regard to the return springs 32, 33, in that they are not tied but act directly on the pistons opposite one another. It may be advisable to design the bottom 11 of the cylinder opening 13 in such a way that the spring can engage there or at least is held in place by static friction. 2 and 4, the end of the spring is chamfered to match the pitch of the coil to the ground so that the force is transmitted precisely along the longitudinal axis of the cylinder.
  • the attack areas 50, 51 on the piston 1 or on the housing 15 can also be provided with projections in which the springs can snap into place. Another possibility, as already explained above, is to use the features according to FIG. 1 with regard to the return springs.
  • seals 6, 7 and 12, 14 with their sealing foot 25, 26 bear against the inner end face 22, 23 and 30, 31 of the associated annular groove 16 to 19 and support them there. Since these inner end faces are integrally connected to the housing 15, they can absorb considerable forces in a small installation space.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)

Abstract

L'invention concerne un maître-cylindre tandem (20) à deux pistons plongeurs aspirants (1, 3) et vise à en concevoir le montage le plus simple et le plus économique possible. A cet effet, des gorges de retenue (16 à 19) annulaires sont disposées directement dans le carter (15) du maître-cylindre (20) pour recevoir les joints d'étanchéité (6), à savoir à la fois le joint primaire (6) et, dans un mode de réalisation plus élaboré concernant le joint primaire (7) du piston situé du côté de la tige de compression, les joints secondaires (12, 14) des deux pistons (1, 3). Des perfectionnements supplémentaires concernent des gorges d'anneaux collecteurs (45, 46) à la hauteur des orifices de raccordement pour le réservoir de compensation (5, 10).
EP01960530A 2000-07-28 2001-07-21 Maitre-cylindre de frein a pistons plongeurs aspirants et gorges radiales integrees dans le carter pour recevoir les joints d'etancheite Withdrawn EP1409319A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10037279 2000-07-28
DE10037279 2000-07-28
DE10120913 2001-04-27
DE10120913A DE10120913A1 (de) 2000-07-28 2001-04-27 Hauptbremszylinder mit Plungerkolben und in das Gehäuse eingefügten Radialnuten zur Aufnahme der Dichtmanschetten
PCT/EP2001/008441 WO2002009992A1 (fr) 2000-07-28 2001-07-21 Maitre-cylindre de frein a pistons plongeurs aspirants et gorges radiales integrees dans le carter pour recevoir les joints d'etancheite

Publications (1)

Publication Number Publication Date
EP1409319A1 true EP1409319A1 (fr) 2004-04-21

Family

ID=26006568

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01960530A Withdrawn EP1409319A1 (fr) 2000-07-28 2001-07-21 Maitre-cylindre de frein a pistons plongeurs aspirants et gorges radiales integrees dans le carter pour recevoir les joints d'etancheite

Country Status (3)

Country Link
US (1) US7168536B2 (fr)
EP (1) EP1409319A1 (fr)
WO (1) WO2002009992A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006013626A1 (de) * 2005-03-23 2006-10-05 Continental Teves Ag & Co. Ohg Elektrohydraulische Bremsanlage mit Fahrdynamikregelung
US7197874B2 (en) * 2005-08-02 2007-04-03 Continental Teves, Inc. Plunger master brake cylinder
DE102005039659B3 (de) 2005-08-22 2007-01-11 Lucas Automotive Gmbh Hauptbremszylinderanordnung für eine hydraulische Kraftfahrzeugbremsanlage mit teleskopierbarer Kolbenanordnung und Kraftfahrzeugbremsanlage
US20090013685A1 (en) * 2007-07-11 2009-01-15 Molenaar Kelly J Master cylinder for vehicle brake system
US9657753B2 (en) 2011-06-17 2017-05-23 Bwi (Shanghai) Co., Ltd. Master cylinder assembly in brake system
JP5507532B2 (ja) * 2011-11-25 2014-05-28 日信工業株式会社 マスタシリンダ装置
US9393942B2 (en) 2013-11-01 2016-07-19 Beijingwest Industries, Co., Ltd. Composite spring retainer and method of assembly in a brake master cylinder

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2569025A (en) 1946-12-07 1951-09-25 Bendix Aviat Corp Master cylinder sealing and compensating means
US2715555A (en) * 1953-04-09 1955-08-16 Ramsey Corp Compression piston ring
US3887198A (en) * 1973-10-26 1975-06-03 Caterpillar Tractor Co Pressure balanced ring seal
IT1043308B (it) 1975-10-13 1980-02-20 Benditalia Spa Cilindro maestro per veicoli automobilistici
US4289264A (en) * 1979-03-23 1981-09-15 The United States Of America As Represented By The Secretary Of The Air Force Uniform load piston ring
ES8103698A1 (es) * 1980-07-30 1981-03-16 Bendiberica Sa Perfeccionamientos en cilindros maestros para instalaciones de frenos hidraulicos de vehiculos
US4337956A (en) * 1980-12-30 1982-07-06 American Sterilizer Company Double lip seal with pressure compensation
JPS58191662A (ja) 1982-04-30 1983-11-08 Aisin Seiki Co Ltd タンデムマスタシリンダ
US4503677A (en) * 1982-05-20 1985-03-12 Allied Corporation Master cylinder
ES532679A0 (es) * 1984-05-22 1985-04-01 Bendiberica Sa Perfeccionamientos en cilindros maestros tandem hidraulicos
US4790138A (en) * 1987-02-03 1988-12-13 Allied-Signal Inc. Master cylinder fast fill valving mechanism with ramp
JPH0217203A (ja) * 1988-07-05 1990-01-22 Jidosha Kiki Co Ltd 流体アクチュエータ
US4945728A (en) * 1989-06-26 1990-08-07 General Motors Corporation Center compensating tandem master cylinder with seals in cylinder wall
DE4120668C2 (de) 1991-06-22 1997-04-24 Ebern Fahrzeugtech Gmbh Tandem-Hauptzylinder
DE4137461C2 (de) * 1991-11-14 1994-06-16 Freudenberg Carl Fa Dichtungsanordnung für einen Separator
JPH06305409A (ja) * 1993-04-23 1994-11-01 Jidosha Kiki Co Ltd マスタシリンダ
US6012288A (en) * 1995-12-20 2000-01-11 Kelsey-Hayes Company Master cylinder having radially formed end plugs and press-fit caged spring assembly pin
DE19626926B4 (de) 1996-07-04 2006-03-16 Continental Teves Ag & Co. Ohg Elektronisch regelbares Bremsbetätigungssystem

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0209992A1 *

Also Published As

Publication number Publication date
US7168536B2 (en) 2007-01-30
US20040011614A1 (en) 2004-01-22
WO2002009992A1 (fr) 2002-02-07

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