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
  • F16D65/005—Components of axially engaging brakes not otherwise provided for
  • F16D65/0087—Brake housing guide members, e.g. caliper pins; Accessories therefor, e.g. dust boots
• • 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
  • F16J3/00—Diaphragms; Bellows; Bellows pistons
  • F16J3/04—Bellows
  • F16J3/041—Non-metallic bellows
  • F16J3/046—Lubrication or venting 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
  • F16D2121/00—Type of actuator operation force
  • F16D2121/02—Fluid pressure
  • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
• • 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
  • F16D2125/00—Components of actuators
  • F16D2125/02—Fluid-pressure mechanisms
  • F16D2125/08—Seals, e.g. piston seals
• • 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
  • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc 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
  • F16D65/14—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

Definitions

• the present invention relates to a resilient boot sealing system for an automotive wheel brake actuation cylinder.
• wheel brake cylinders are generally fix with a stator e.g. mounted fix to an axle, anchor plate or else and may be embodied as hydraulic, electric or mechanic actuator including a relatively movable actuation member for initiating spread operation between brake pads, such as brake shoes.
• a stator e.g. mounted fix to an axle, anchor plate or else and may be embodied as hydraulic, electric or mechanic actuator including a relatively movable actuation member for initiating spread operation between brake pads, such as brake shoes.
• conventional drum brakes for vehicles are widely known and often comprise hydraulic wheel brake cylinder with a housing, hydraulic pressure chamber and mostly two hydraulically actuated diametrically working pistons as the responsible actuation members for spreading brake shoes.
• Each piston performs in form of a displaceable wall that limits the hydraulic fluid volume capacity in the pressure chamber of the housing.
• the hydraulic pistons spread between two brake shoes under hydraulic pressure when the drum brake system is
• a parking brake function mode may operate with the same cylinder together with added self locking means. Consequently the brake shoes are urged to get in frictional contact with the sliding surface of the rotating brake drum. Pretensioned return springs serve for return/retention of the brake shoes including pistons when the drum brake is released.
• any relative displacement between housing and actuation member requires a gap inbetween and that gap requires a sealing system which includes a flexible boot comprising interfaces concerning the periphery with bellows arranged between the said interfaces so that ingress of foreign substance is flexibly avoided.
• a general problem with respect to those cylinders is their inexpensive durability under improved resistance against corrosion. That task is not easy to achieve because wheel cylinder are mostly located in relatively basic (low level) niches which means that the cylinders are placed in an area which is exposed to weather and dirt. Well protection against contamination with foreign substance, such as dirt, fluid, gravel or mixtures thereof is key.
• a conventional dust boot is an example for regular components of conventional wheel cylinders on hydraulic drum brakes, electric parking brakes and combined brakes .
• Such boot is responsible to avoids dust entrance to the wheel cylinder interior. That prevents damages concerning sealing or guidance between actuation member (mostly a hydraulic sealed piston) and cylinder.
• a defective boot may cause con tamination of hydraulic brake fluid or risk that brake fluid leaks and spoils the exterior.
• High pressure spray cleaning systems may be of significant danger due to possible ingress of cleaning fluids.
• JP 3938236 B2 discloses a drum brake cable actuation interface member with a sealing system including a boot device that comprises two interface sections that are each mounted from radially outwards (centered radially outwardly) on periphery and wherein one of the interface sections is per forated .
• the flexible boot has bellows between the interface sections and allows relative displacement between actuation member and housing .
• Brake cable linkage may be introduced from a backside of the housing .
• the interface section integrates a tiny through hole orifice, which provides constant pressure equalization between internal and external of the boot . Con sequently such hermetically open boot design avoids uncontrolled flipping action . For this reason an extra supplemental shielding wall is suggested, which is arranged on the radially outer housing interface portion of the boot, for extra protection against ingress of rainwater or spray water e.g. washing fluids .
• US 3,187,848 discloses heat resistive and also robust mounting improvement for drum brake wheel cylinders together with a housing having a cylinder bore provided therein, a piston operable in said bore and forming therewith fluid pressure chamber, one end of said housing adj acent said cylinder having a cylindrical recess formed therein of larger length and diameter than said cylinder bore whereby a protective shoulder is provided, the annular inner surface of said recess having a predetermined controlled micro finish of greater roughness than said cylinder bore, a link pin in engagement with said piston and extending through and beyond said cylinder for actuation of a brake shoe, so that an annular wheel cylinder boot is integrated in the housing .
• the packaging is improvable and test programs reveal weakness with respect to protection against contamination, especially weakness in protection against ingress of fluids like rainwater, pressurized spray washing water or weakness in passing salt-spray-corrosion-tests. That weakness appears in connection with uncontrolled flipping of the boot.
• An object of the present invention is a sealing system im provement, together with optimized thermal design. Specific further object is improvement in protection against ingress of foreign substance e.g. fluid which means inhibit internal corrosion or spoil. Consequently improved substance protection against ingress of foreign substance, while avoiding the drawbacks of the prior art are major objects of the present invention . Also an actualized, reasonable, easy to mount, valuable and by the way cost responsible designchange concerning the sealing system is requested, which especially avoids risk for ingress of substance when flipping action occurs .
• a sealing system that is provided with pressure relief valve means and with integrated pressure relief valve function which is normally closed and automatically and temporarily changes in a controlled, limited and also reversible manner into open status for pressure relief when pressure is not equal between interior and exterior .
• the invention provides for pressure balance between interior and exterior . Balance avoids or limits boot deformation and consequently flipping of the boot .
• the invention is linked with the exclusive benefit, that dust boot drop out from cylinders exterior housing seat is effectively eliminated .
• pressure relief valve mode is changed automaticly, selfdriven, without supply of external energy, especially currentless but still in a predetermined, controlled matter, so that the benefits are earned suprisingly simple in serial applications.
• the pressure relief means of the sealing system integrates relief valve spring elasticity wherein the relief valve elasticity which is integrated in the elastomere, flexible dust boot, and that peripheral interface of the dust boot integrates relief valve body means, so that a part of the radially grooved counterpart seat of housing and/or acutating member/piston integrates a relief valve seat of the respective relief valve.
• the pressure relief valve body in the interface section of the boot may be configured as a separate recessed portion of the boot, and wherein the recessed portion is connected with interior but separated from exterior. Consequently the periphery of the boot may be unchanged and all mechanical design change may con centrated on a change of the elastomeric boot.
• the boot is made from rubber or other elastomere material, such designchange is relatively easy so that a cheap change of the boot during maintenance will allow that conventional cylinders (including their periphery) will effectively earn all benefits of the present invention.
• a tooling of the boot is simplyfied, when the boot includes a recessed portion in its interface section, that is embodied as a longitudinal slot section which is arranged in parallel with the linear displacement direction of the actuation member.
• Another alternative embodiment of the invention may include a recessed portion integrated in its interface section, that can be embodied as a longitudinal slot section comprising antiparallel slot design with walls that can be inclinded or curved with respect to a central axis of linear displacement. The effect of the latter is an extended slot length so that improved sealing function against ingress of foreign substance is achieved .
• Elasticity in valve function is easily changed by simple change of thickness of an orthogonally arranged end wall/diaphragm.
• the end wall/diaphragm is provided with a specific, given resilience, and that the resilience of the end wall corresponds with the necessary elasticity of the relief valve means. Consequently the end wall may be designed with reduced wall thickness in compare with an average wall thickness of the boot.
• Performance of the relief valve may effectively be improved when an interface portion integrates multiple recessed portions and/or slot sections.
• pressure relief valve means are integrated only on the first interface portion, or integrated only on the second interface portion or alternatively integrated on both interface portions.
• Further adaption is possible, when multiple slot sections and/or interface portions are regularily arranged, especially under equivalent distance and with equivalent angle to each neighbour on the boot. It is further beneficial when pressure relief valve means are in tegrated in all interface sections of a boot.
• Fig. 1 is an isometric sectional view depicting a first embodiment of a hydraulic wheel cylinder with sealing means according to the present invention and when actuation members (pistons) are fully retracted,
• FIG. 2 shows the same cylinder as in Fig. 1 with expanded compression spring between the both actuation members
• Fig. 3 is an exploded isometrical view of the cylinder components
• Fig. 4 is an exploded isometrical view of parts that form the both actation members of the cylinder in Fig. 1,
• Fig. 5b is an enlarged, transverse, sectional detail view concerning cylinder and boot details as marked V in Fig. 5a concerning the first embodiment
• Fig. 6a is an enlarged front view and Fig. 6b is an isometric view of the boot with integrated slots in its second, radial inner, interface area (first embodiment) ,
• Fig. 7 is an enlarged, transverse, sectional view concerning cylinder and boot details as marked V in Fig. 2 concerning the second boot embodiment (integrated slots in first, radial outer, interface area) ,
• Fig. 8a, b is an enlarged front view and Fig. 8b) is an isometric view of the boot embodiment in Fig. 7 comprising integrated slots in its first interface area (second boot embodiment) ,
• Fig. 11 a,b + 12 a,b further variation in embodiments comprising antiparallel (inclined) slot (Fig. 11 a, b - in sectional view) and irregular positioned slots (Fig. 12 a, b - isometric view) .
• a drum brake system according to the present invention may principally be designed in simplex, duplex, duo-servo or other constructive mechanical configuration.
• a drum brake systems according to the invention may generally be operated in different functions according to very different functional modes e.g. in service brake mode and/or in self-locking parking brake mode, and /or in emergency brake mode in redundancy to a service brake system.
• a drum brake system comprises two opposed and relatively to each other expandable brake shoes that may frictionally cooperate in brake actuation with the circumferential friction surface of a rotatable brake drum that stands in association with a rotatable vehicle wheel (not shown) .
• a wheel cylinder 3 is configured as linear drive, e.g. expander that may include hydraulic, mechanic and/or electromechanical subsystems e.g. an electromotive actuator with drive train e.g. gears in stages and /or rotation-to -translation exchange, together with other suitable brake periphery e.g. drum brake linkage means .
• Each cylinder 3 comprises at least single or opposed displaceable actuation members 5,6.
• the cylinder 3 is generally rotationally fix to a drum brake stator which may be designed in typical anchor plate shape or alternatively designed as axle component.
• the cylinder 3 may be designed as a hollow solid body arranged with mechanical interface with comprising the mounting socket 16 and integrated internal thread 17 for externally threaded mounting means such as screws .
• each cylinder is arranged with electric and/or hydraulic port means 18 that may be designed as interface connector e.g. internal thread, bleeding valve means 19 in the vertically uppermost portion of a hydraulic chamber 20 , the hydraulic chamber 20 standing in permanent hydraulic connection with the hydraulic port 18 , longitudinal cylinder bore 21 and also with two opposed hydraulic action member pistons that are allocated for sealed axial relative displacement within the cylinder bore .
• Each actuation member piston carries its own sliding lip seal member 22,23.
• a compression spring member 24 may be allocated interposed in axially between the two actuation member pistons so that the both pistons are generally and flexibly spread apart from each other for safeguarding the nominal hydraulic chamber volume when the brake system remains driveless under brake release condition .
• the ends of the compression spring member 24 may be allocated in opposed blind bores 25,26 of the both actuation member pistons .
• the cylinder comprises an annular flexible ring shape sealing boot 1,2 that integrates at its first end a housing interface 9 including a radially inwardly directed flange 27 which is elastically snapped and thereby sealingly allocated in a radially lowered position from radially outwardly into a radial groove of a seat 12 that is arranged on the outer surface of the expander housing 4.
• a second end of the ring shape sealing boot 1,2 is configured with a member interface 10 including a radially inwardly directed flange 28 that is elastically snapped and thereby sealingly allocated in a radially lowered position from radially outwardly into a groove of a seat 13 that is arranged on an outer surface of the actuating member (piston) 5,6.
• both seats 12,13 and interface portions 9,10 form an overlapping, lowered, meander- shape mechanical in- teracting sealing system for improved mechanical spray water resistance, which is additive to flexible, elastomere sealing means/functions that are integrated in each flange 27,28 of the boot 1,2. Consequently the described sealing system provides the generally hermetical (dustproof, liquidtight, gastight) sealing function between interior (e.g. "dry" room 11,11') and exterior E.
• An interface 9,10 of the boot additionally comprises normally closed pressure relief valve means and implicit pressure relief valve function which means that the valve body automatically and temporarily changes in predetermined position into open status under a pressure gradient decline in direction from interior of room 11,11' to exterior E with respect to the room 11,11' which is separated inbetween boot 1,2 and housing 4. Consequently the sealing system allows predetermined, controlled and by this way also limited, directed, overpressure release e.g. gas blow out from the room 11,11' into the exterior E.
• a very specially designed section of the boots flanges 27,28 manages directed blow out when integrating additional feature and function, as its valve body is temporarily allowed to be temporarily lifted above its opposed valve seat nutground section.
• bootintegrated elastomere check valve function terminates as it closes under equal pressure between room 11,11' interior and exterior E.
• the boots 1, 2 "valve body" flange portion automatically returns after blow out into its sealed normally closed sealing position with respect to the seat 12,13 in the nutground section. All that function is performed automatically with elastomere elasticity of the inventive boot 1,2 only under the influence of pres suregradient . Consequently the invention works selfmotivated, without supply of external energy, especially currentless.
• the pressure relief valve body (flange portion) of the boot integrates a separate recessed slot/channel shape section 14, and wherein that recessed portion 14 is normally connected with internal room 11,11' and also normally sealingly separated from exterior E by flexible, thinned diaphragm/end wall 15.
• the radially inner, integrated, recessed, portion 14 in the flange 27, 28 may be embodied as a longitudinal slot section which is arranged in parallel with the axial, linear displacement direction of the actuation member 5, 6 and wherein each diaphragm is arranged as a flexible end wall 15 that is arranged generally orthogonal with respect to the axial axis of displacement.
• Each end wall 15 is provided with a specific, predetermined re silience, and that the resilience of the diaphragm/end wall 15 corresponds with the necessary elasticity with respect of the pressure difference control.
• the end wall/diaphragm 15 may especially be designed with reduced wall thickness in compare with an average wall thickness dm of the boot 1,2.
• An interface section 9,10 of a boot 1,2 may comprise multiple pressure relief valve sections, which means that one interface portion 9,10 may integrate multiple recessed portions 14 and/or slot sections.
• the multiple valve body portions/slot sections 14 are preferably regularily arranged, and they may especially be under equal distance and in circumferential direction be arranged with equal angle to each other/neighbour slot.
• the behaviour of the valve function may be influenced by the overall number of the slots, the area/size of the slots, and the elasticity of their diaphragm/end wall 15.
• Fig. 11 and 12 concentrate on further valuable detail variations with respect to a boot 1 that are disclosed in example in connection with the first embodiment of the boot 1.
• Fig. 11 a, b show antiparallel slot 13 design modification comprising inclined slot orientation with regard to the central axis of displacement.
• Fig. 12 a, b disclose irregular applications of the inclined slot 13 design modification.
• the pressure relief valve means may be integrated within the second interface portion 10 of boot 1 only (as shown in Fig. 1-5) , or the relief valve means may be integrated in the first interface portion 10 of boot 2 only (as shown in Fig. 7+8) .
• all interface portions 9,10 of a boot may include pressure relief valve means so that uncontrolled displacement (flipping) of the dust boot is most effectively avoided.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Sealing Devices (AREA)
• Diaphragms And Bellows (AREA)
• Braking Arrangements (AREA)

Priority Applications (9)

Applications Claiming Priority (1)

Related Child Applications (1)

Publications (1)

Family

ID=63840799

Family Applications (1)

Country Status (8)

Cited By (1)

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Citations (9)

Family Cites Families (34)

• 2018
  • 2018-09-28 KR KR1020217005399A patent/KR20210031978A/ko not_active Ceased
  • 2018-09-28 PL PL18785869.1T patent/PL3857092T3/pl unknown
  • 2018-09-28 WO PCT/EP2018/076450 patent/WO2020064124A1/en not_active Ceased
  • 2018-09-28 CN CN201880098237.4A patent/CN112888872B/zh active Active
  • 2018-09-28 ES ES18785869T patent/ES3017782T3/es active Active
  • 2018-09-28 EP EP18785869.1A patent/EP3857092B8/en active Active
  • 2018-09-28 JP JP2021511567A patent/JP7177252B2/ja active Active
• 2021
  • 2021-03-29 US US17/216,217 patent/US12241512B2/en active Active

Patent Citations (9)

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