WO1992008898A1 - Mecanisme a piston d'actionnement de frein comportant une double zone - Google Patents

Mecanisme a piston d'actionnement de frein comportant une double zone Download PDF

Info

Publication number
WO1992008898A1
WO1992008898A1 PCT/US1991/008031 US9108031W WO9208898A1 WO 1992008898 A1 WO1992008898 A1 WO 1992008898A1 US 9108031 W US9108031 W US 9108031W WO 9208898 A1 WO9208898 A1 WO 9208898A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
bore
accordance
disposed
housing
Prior art date
Application number
PCT/US1991/008031
Other languages
English (en)
Inventor
Raymond Joseph Black
Original Assignee
Allied-Signal Inc.
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 Allied-Signal Inc. filed Critical Allied-Signal Inc.
Priority to JP4500874A priority Critical patent/JPH06501537A/ja
Publication of WO1992008898A1 publication Critical patent/WO1992008898A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16D65/543—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment comprising a plastically-deformable 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
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/007—Auxiliary mechanisms for non-linear operation

Definitions

  • This invention relates generally to a hydraulic brake actuation piston mechanism, and in particular to a dual area brake actuation piston mechanism for aircraft brake assemblies.
  • Aircraft disc brake assemblies are conventionally full circle configurations which incorporate a plurality of piston mechanisms in a balanced arrangement about the circle and which operate to move a pressure plate into engagement with a disc brake stack comprised of alter- nating stationary and rotating disc elements.
  • Prior actuation piston mechanisms conventionally employ a single piston which results in a linear relationship between the disc interface pressure and the brake system pressure.
  • a dual area brake actuation piston mechanism comprising a housing having therein first and second bores, the second bore disposed within and coaxial with said first bore, a first piston mechan ⁇ ism disposed in said first bore and extending from the bore to a piston end, a second piston disposed within said second bore and extending to said piston end, and respective first and second bore openings in the housing to permit fluid flow communication with said bores, the
  • SUBSTITUTESHEET second bore opening containing valving means which con ⁇ trols fluid flow into said second bore, so that fluid pressure communicated with said bore openings causes said first piston to displace said piston end and increased fluid pressure causes said second piston to be displaced against said piston end such that the piston end is dis ⁇ placed conjointly by both pistons.
  • Figure 1 is a sectional schematic representation of an actuation piston mechanism embodying the present invention
  • Figure 2 is a sectional schematic representation of an alternative valving means that may be utilized in the present invention.
  • Figure 3A is a graph illustrating a typical relationship between input pressure (P-P ) and time;
  • Figure 3B is a graph illustrating the relation- ship between the effective piston area and time according to the pressure history shown in Figure 3A;
  • Figure 4 is a graph illustrating the relationship between effective piston area and pressure input for an actuation piston mechanism utilizing the valving mechanism of Figure 2;
  • Figure 5 is an alternative embodiment of the present invention.
  • Piston housing 12 comprises rear piston housing 14 threadedly engaged with front piston housing 16 by means of threaded connection 18.
  • Rear piston housing 14 defines with front piston housing 16 fluid pressure receiving man ⁇ ifold chamber 20 having fluid passage 22. Chamber 20 is sealed by sealing mechanism 24.
  • Front piston housing 16 comprises first piston bore 30 disposed coaxially about second piston bore 40. Each bore 30, 40 is open ended so that first piston 50 may extend from the first bore and second piston 60 may extend from the second bore.
  • First bore 30 includes first bore opening 32 which communicates with chamber 20.
  • First piston 50 comprises interior piston end 52 having opposing grooves 54 receiving therein sealing means 56 each of which engages radially opposed wall surfaces 57 and 59 of the first bore.
  • First piston 50 extends axially to abut piston end 70. Piston 50 and piston end 70 are connected by ring 72, and piston 50 is engaged by wiper 17 mounted in groove 19 of first housing 16.
  • Second piston 60 comprises interior piston end 62 having groove 64 receiving sealing mechanism 66 which engages the surface of second bore 40. Second piston 60 extends axially to engage piston 70 at end bumper member 65 (which may be metallic, elastic, or otherwise such as a composite material) , and is engaged by wiper 21 located within groove 23 of first housing end 16.
  • Piston end 70 includes axial extension 74 which extends interiorly of second piston 60 to engage and be coupled with the second piston.
  • piston end 70 includes short axial extension 76 which engages the outer axial surface of second piston 60.
  • Second bore 40 includes bore opening.
  • Valving means 80 comprises valve member 82 having flow restriction orifice 84, valve member 82 being biased by resilient means 86 into engagement with valve seat 88.
  • Valving means 80 restricts fluid flow from chamber 20 through second bore opening 42 and into second bore 40 while permitting increased fluid flow in the reverse direction at and above a predetermined pressure differential which causes valve member 82 to disengage from valve seat 88 during brake release.
  • Adjuster mechanism 90 may be disposed within first bore 30. Adjuster mechanism 90 comprises engagable member 92
  • SUBSTITUTESHEET and engaging member 94 which comprises a radial abutment of first housing 16.
  • Flange member 96 of mechanism 90 abuts ring 97 attached to first piston 50, and engages engagable member 92 by way of resilient means 98 which extends between flange 96 and radial shoulder 58 of the first piston.
  • Actuation piston mechanism 10 provides at low braking pressures (when brake effectiveness is high) the actuation of first piston 50 via piston area Al defined by interior piston end 52 located within first bore 30. At higher fluid pressures when the brake effectiveness would typi ⁇ cally not be as high, second piston 60 is actuated by fluid pressure acting upon area A2 such that the effective piston area is Al plus A2 which displaces piston end 70 against the not shown brake pressure plate. Actuation piston mechanism 10 would alleviate brake grabbiness due
  • Figure 3B illustrates graphically the relation ⁇ ship between the effective piston area and time.
  • FIG. 2 illustrates an alternative embodiment of a valving means or mechanism 180 that may be utilized in the actuation piston mechanism of the present inven ⁇ tion.
  • a poppet valve comprising housing 142 receives therein poppet 182 biased by resilient means 186 against valve seat 188.
  • Valving means 180 will keep low fluid pressure from being communicated effectively to second bore 40. However, higher fluid pressures at and above a predetermined pressure level will cause poppet 182 to disengage from valve seat 188 and permit the higher pres ⁇ sures to be communicated to second bore 40.
  • Poppet head 182 includes small opening 183 which will permit fluid to flow back to chamber 20 once poppet head 182 has reengaged valve seat 188 at the predetermined pressure level.
  • Figure 4 illustrates graphically the relationship between the effective piston area and the pressure input in chamber 20 when valving means 180 of Figure 2 is uti ⁇ lized within actuation piston mechanism 10.
  • first piston 50 is displaced such that effective piston area Al corre ⁇ sponds to a pressure output indicated by portion Al of graph A.
  • valving means 180 has opened at the prede- termined pressure level, effective piston area A2 of second piston 60 combines with effective piston area Al to provide a pressure output indicated by portion Al + A2 of curve A.
  • the main difference between valving means 80 and 180 is that valve means 180 will provide a stepped pressure curve rather than the increase in pressure illustrated in Figure 3B.
  • FIG. 5 illustrates an alternative embodiment of the present invention. Most similar structure is indicated by the same reference numeral increased by 100.
  • the adjuster mechanism indicated by reference numeral 190 is disposed within the second piston 160.
  • Housing 112 of piston mechanism 110 includes ball-and-tube extension 194 which is engaged by engagable member 192.
  • Second piston 160 includes ring 197 that serves as a seat for flange 196 biased by resilient means 198.
  • Resilient means 198 is disposed between flange 196 and radial shoulder 167 of the second piston.
  • Second piston 160 includes a second sealing mechanism 168 engag ⁇ ing sealingly ball-and-tube mechanism 194 and separate from sealing mechanism 166 disposed within groove 164.
  • Second piston 160 also includes threaded end 163 which engages threads 172 of piston end 170, so that piston end 170 does not move relative to second piston 160.
  • Second piston bore 140 receives fluid pressure via valving means 80.
  • Mechanism 110 operates similar to the mechanism of Figure 1 and as represented by the graphs of Figures 3A and 3B. Alternatively, mechanism 110 may include the valving means or mechanism 180 illustrated in Figure 2 rather than valving means 80.

Landscapes

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

Abstract

Le mécanisme à piston d'actionnement de frein comportant une double zone (10, 110) comprend un carter de piston (12, 112) dans lequel se trouve un premier passage (30, 130) disposé de manière coaxiale autour d'un second passage séparé (40, 140). Un premier piston (50, 150) est placé à l'intérieur du premier passage (30, 130) et s'étend à partir du premier passage (30, 130) vers une extrémité de piston (70, 170). Un second piston (60, 160) est placé dans le second passage (40, 140) et s'étend de manière à prendre appui sur l'extrémité de piston (70, 170). Les passages (30, 40; 130, 140) sont pourvus de premières et secondes ouvertures de passage (32, 42; 132, 142) destinées à recevoir un fluide pressurisé qui déplace les pistons respectifs (50, 60; 150, 160). Une fois que le premier piston (50, 150) a été actionné par des pressions de fluide plus faibles, une pression de fluide plus forte provoque le déplacement du second piston (60, 160) contre l'extrémité de piston (70, 170) de sorte que celle-ci est déplacée conjointement par les deux pistons (50, 60; 150, 160). Le mécanisme à piston (10, 110) peut comprendre un mécanisme de réglage (90, 190) situé dans le carter (12, 112).
PCT/US1991/008031 1990-11-08 1991-10-30 Mecanisme a piston d'actionnement de frein comportant une double zone WO1992008898A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP4500874A JPH06501537A (ja) 1990-11-08 1991-10-30 複面積ブレーキ作動ピストン機構

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US61067190A 1990-11-08 1990-11-08
US610,671 1990-11-08

Publications (1)

Publication Number Publication Date
WO1992008898A1 true WO1992008898A1 (fr) 1992-05-29

Family

ID=24445968

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1991/008031 WO1992008898A1 (fr) 1990-11-08 1991-10-30 Mecanisme a piston d'actionnement de frein comportant une double zone

Country Status (2)

Country Link
JP (1) JPH06501537A (fr)
WO (1) WO1992008898A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2730024A1 (fr) * 1995-01-31 1996-08-02 Alliedsignal Europ Services Frein a disque a absorption reduite
EP0838603A1 (fr) * 1996-10-24 1998-04-29 Wichita Company Limited Actionneur pour un dispositif de freinage
FR2761742A1 (fr) * 1997-04-03 1998-10-09 Bosch Syst Freinage Systeme de freinage a absorption reduite
WO1999006729A1 (fr) * 1997-08-01 1999-02-11 Alliedsignal Inc. Dispositif de reglage automatique interne sans axe pour piston de frein
US10267369B2 (en) 2017-07-28 2019-04-23 Akebono Brake Industry Co., Ltd Articulating brake piston cap for a brake assembly

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8262057B2 (en) * 2007-06-15 2012-09-11 Fisher Controls International, Llc Flow controlled actuator apparatus for use with self-closing stop valves

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3068841A (en) * 1961-01-13 1962-12-18 Robbins & Bendror Associates I Hydraulic pressure system
US3650364A (en) * 1969-07-18 1972-03-21 Borg Warner Ltd Friction coupling with dual pistons
US4496033A (en) * 1981-12-28 1985-01-29 Goodyear Aerospace Corporation Dual piston actuator
US4704947A (en) * 1985-10-21 1987-11-10 Versa Technologies, Inc. Bidirectional fluid flow valve
US4753136A (en) * 1985-01-19 1988-06-28 Aisin-Warner Limited Hydraulic control of transmission
US4815359A (en) * 1987-12-17 1989-03-28 Allied-Signal Inc. Compact brake piston return mechanism

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3068841A (en) * 1961-01-13 1962-12-18 Robbins & Bendror Associates I Hydraulic pressure system
US3650364A (en) * 1969-07-18 1972-03-21 Borg Warner Ltd Friction coupling with dual pistons
US4496033A (en) * 1981-12-28 1985-01-29 Goodyear Aerospace Corporation Dual piston actuator
US4753136A (en) * 1985-01-19 1988-06-28 Aisin-Warner Limited Hydraulic control of transmission
US4704947A (en) * 1985-10-21 1987-11-10 Versa Technologies, Inc. Bidirectional fluid flow valve
US4815359A (en) * 1987-12-17 1989-03-28 Allied-Signal Inc. Compact brake piston return mechanism

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2730024A1 (fr) * 1995-01-31 1996-08-02 Alliedsignal Europ Services Frein a disque a absorption reduite
EP0725226A1 (fr) * 1995-01-31 1996-08-07 Alliedsignal Europe Services Techniques Frein à disque à absorption réduite
EP0838603A1 (fr) * 1996-10-24 1998-04-29 Wichita Company Limited Actionneur pour un dispositif de freinage
FR2761742A1 (fr) * 1997-04-03 1998-10-09 Bosch Syst Freinage Systeme de freinage a absorption reduite
WO1999006729A1 (fr) * 1997-08-01 1999-02-11 Alliedsignal Inc. Dispositif de reglage automatique interne sans axe pour piston de frein
US6016892A (en) * 1997-08-01 2000-01-25 Alliedsignal Inc. Pinless internal automatic adjuster for brake piston
US10267369B2 (en) 2017-07-28 2019-04-23 Akebono Brake Industry Co., Ltd Articulating brake piston cap for a brake assembly

Also Published As

Publication number Publication date
JPH06501537A (ja) 1994-02-17

Similar Documents

Publication Publication Date Title
US4133178A (en) Quick take-up master cylinder
US4939901A (en) Tandem master cylinder with piston stops and central valves
US4664242A (en) Torque transmitting device having a fluid-operated piston
GB2098294A (en) Brake master cylinder
US4631924A (en) Dual-circuit master cylinder having auxiliary piston and yoke with equalization chambers for hydraulic equalization
EP0448548B1 (fr) Mecanisme compact a rappel-piston pour frein
WO1992008898A1 (fr) Mecanisme a piston d'actionnement de frein comportant une double zone
US4724674A (en) Hydraulic brake booster
US5209154A (en) Dual area brake actuation piston mechanism
US4848527A (en) Inertial brake unit for air clutch
GB2041127A (en) Hydraulic pressure control valve assembly for dual circuit braking systems
GB2076487A (en) A quick take-up master cylinder for an automotive vehicle
US4534172A (en) Master cylinder assembly for a vehicle hydraulic braking system
CA1037523A (fr) Repartiteur modulaire
CA1089513A (fr) Maitre-cylindre tandem avec soupape integree de repartition
US4609230A (en) Dual brake valves
US4736989A (en) Dual deceleration and pressure-sensitive proportioning valve
CA1301080C (fr) Ratrappe-jeu hydraulique
CA1164511A (fr) Maitre cylindre de systeme de freins hydrauliques pour vehicules
EP0402355B1 (fr) Soupape primaire de dosage a pression equilibree
US4569271A (en) Hydraulic boosters for vehicle hydraulic systems
US4821519A (en) Primary pressure-balanced proportioning valve
EP0008909B1 (fr) Commande combinée d'embrayage et de freinage
US4498710A (en) Dual brake valves
GB2072286A (en) Proportioning valves for vehicle brakes

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LU NL SE

122 Ep: pct application non-entry in european phase