WO2004109143A1 - Systeme de frein a disque humide refroidi par fluide - Google Patents

Systeme de frein a disque humide refroidi par fluide Download PDF

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Publication number
WO2004109143A1
WO2004109143A1 PCT/AU2004/000756 AU2004000756W WO2004109143A1 WO 2004109143 A1 WO2004109143 A1 WO 2004109143A1 AU 2004000756 W AU2004000756 W AU 2004000756W WO 2004109143 A1 WO2004109143 A1 WO 2004109143A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake system
stator
wet brake
disc
fluid
Prior art date
Application number
PCT/AU2004/000756
Other languages
English (en)
Inventor
Stan Nowak
Dorota Helena Kieronska
Vin C. Morley
Original Assignee
Safe Effect Pty Ltd
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 Safe Effect Pty Ltd filed Critical Safe Effect Pty Ltd
Priority to AU2004245580A priority Critical patent/AU2004245580B2/en
Priority to CA002527738A priority patent/CA2527738A1/fr
Publication of WO2004109143A1 publication Critical patent/WO2004109143A1/fr
Priority to US11/526,066 priority patent/US20080047786A1/en

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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/228—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a separate actuating member for each side
    • 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
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1324—Structure carrying friction elements
    • 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
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1328—Structure internal cavities, e.g. cooling channels
    • 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
    • F16D65/78—Features relating to cooling
    • F16D2065/784—Features relating to cooling the coolant not being in direct contact with the braking surface
    • 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
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D2069/004—Profiled friction surfaces, e.g. grooves, dimples
    • 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

Definitions

  • the present invention relates to a fluid cooled wet brake system.
  • Wet brake systems are characterised by a sealed housing enclosing a braking surface which is coupled to a rotating body such as a wheel hub, and friction pads which can be forced into engagement with the braking surface.
  • a volume of oil is contained in the housing providing lubrication between the pads and the braking surface.
  • the pads are forced against the braking surface to provide a braking effect with any oil between the pads and the braking surface being expelled.
  • a fluid cooled wet brake system comprising: a sealed housing containing a lubricating liquid; a disc disposed in the housing and adapted for fixing to a rotating body projecting into the housing, the disc having first and second opposite planar surfaces; friction material attached to the first planar surface; a first stator slidably mounted and rotationally fixed within the housing and having a first braking surface facing the first planar surface, the first stator provided with a fluid inlet, a fluid outlet, and one or more internal fluid flow paths extending between the fluid inlet and the fluid outlet through which a cooling fluid flows; and, an actuator for selectively applying a force on the first stator to slide the first stator towards the disc and hold the braking surface against the friction material .
  • the friction material is in the form of one or more pads of fraction material detachably coupled to the disc.
  • the pads are circumferentially spaced apart about the disc.
  • the wet brake system further comprises a second stator having a second braking surface facing the second planar surface and wherein the friction material is attached to the second planar surface, with the second braking surface facing the friction material on the second planar surface, and wherein the actuator selectively applies force on the second stator to slide the second stator toward the disc and hold the second braking surface against the friction material on the second planar surface.
  • a second stator having a second braking surface facing the second planar surface and wherein the friction material is attached to the second planar surface, with the second braking surface facing the friction material on the second planar surface, and wherein the actuator selectively applies force on the second stator to slide the second stator toward the disc and hold the second braking surface against the friction material on the second planar surface.
  • each stator is provided with a plurality of parallel fluid flow paths that extend between the fluid inlet and the fluid outlet.
  • each stator comprises a first annular plate provided with a plurality of channels on one side, and a second annular plate attached to the one side for covering the channels wherein the covered channels form the internal fluid flow paths.
  • the braking system further comprises a mechanism that slidably couples each stator to said housing.
  • each pad is provided with grooves on its surface, where each groove opens at its opposite ends onto an edge of the pad.
  • the braking surfaces are provided with grooves which extend between, and open at their opposite ends, onto respective inner and outer edges of the braking surface.
  • the grooves follow a spiroidal curve.
  • Figure 1 is a transverse section view of an embodiment of the fluid cooled wet brake system
  • Figure 2 is a plan view of a component of a stator incorporated in the wet brake system
  • Figure 3 is a section view of a stator incorporated in the wet brake system
  • Figure. 4 is a front view of a disc incorporated in the wet brake system
  • Figure 5 is a section view of the disc shown in Figure 4.
  • a fluid cooled wet brake system 10 in accordance with an embodiment of the present invention comprises a sealed housing 12 that contains a volume of lubricating liquid such as oil (not shown) and a disc 14 disposed in the housing 12 and adapted for fixing to a rotating body, such as a wheel hub 16 (only a part of which is depicted) disposed in the housing 12.
  • the disc 14 has first and second opposite planar surfaces 18 and 20. Friction material in the form of separate friction pads 22 are attached to the first planar surface 18 of the disc 14.
  • a first stator 24a is slidably mounted and rotationally fixed within the housing 12 and has a first braking surface 26a that faces the first planar surface 18.
  • the first stator 24a is provided with a fluid inlet 28, a fluid outlet 30 and one or more internal fluid flow paths 32 that extend between the fluid inlet 28 and the outlet 30 and through which a cooling fluid such as water or glycol flows.
  • An actuator comprising a set of pistons 34 is held within the housing
  • the cooling fluid flowing through the fluid flow paths 32 can be passed through a radiator or other heat exchanger (not shown) to effectively transfer heat away from the stator 24a and friction pads 22.
  • the system 10 further comprises a second stator 24b which is identical to the first stator 24a but faces the second opposite side 20 of the disc 18.
  • a further set of pistons 34 selectively apply force to the second stator 24b to slide it toward the disc 14 and hold its corresponding second braking surface 26b against friction material in the form of pads 22 fixed to the second surface 20 of the disc 14. It is envisaged that all of the pistons 34 will operate together and thus when the brake is applied, the pistons would force the stators 24a and 24b against friction pads 22 on opposite sides of the disc 14 effectively sandwiching the disc 18. It should be appreciated that in this embodiment the friction pads 22 are attached to the rotating disc 14 while the stators 24a and 24b are rotationally fixed. This is a reversal from the typical arrangement in a wet (or indeed a dry) brake system where the friction material is rotationally fixed and the braking surfaces are the surfaces of a rotating disc, or rotor.
  • each of stators 24a and 24b (hereinafter referred to in general as “stators 24") is in the form of an annular disc comprising the ensemble of a first annular plate 36 and a second annular plate 38.
  • the first plate 36 is formed with a plurality of concentric arcuate channels 42 which extend for approximately 340° about a radial face 40 of a first plate 36.
  • Concentrically adjacent channels 42 are separated by ribs 44.
  • the channels 42 as well as the fluid inlet 28 and fluid outlet 30 are bound by a peripheral wall 46 which extends circumferentially about the radial face for approximately 350°.
  • the wall 46 includes two radially extending wall portions 48.
  • Opposite ends of the ribs 44 are spaced from the wall- portions 48 so as to define respective distribution channels 50 in the general region between the wall portions 48 and adjacent ends of the ribs 44.
  • the fluid inlet 28 is provided in one of the distribution channels 50 with the outlet 30 provided in the other distribution channel 50.
  • the second plate 38 has planar opposite faces and is attached to the first plate 36 over the face 40 to cover, and indeed substantially seal, the channels 42 to thereby define the internal fluid flow paths 32.
  • hoses can be readily coupled to the inlet 28 and outlet 30 to couple the fluid flow paths 32 to a cooling circuit which may include a reservoir of cooling fluid such as water or glycol, a heat exchanger and a pump. Cooling fluid entering through the inlet 28 is distributed by the adjacent distribution channel 50 so as to flow through each of the channels 40 and flow out of the outlet 30.
  • a pair of pins 52 extend axially at diametrically opposed locations from an outer radial surface 54 of the second plate 38 for location in corresponding holes (not shown) formed in the housing 12.
  • the surface 54 forms an outer radial surface of a stator 24.
  • the pins co-axially locate the stators 24 with the disc 14 and allow the stators 24 to slide axially but remain rotationally fixed.
  • Each of the stators 24 thus has planar opposite radial surfaces 26 and 54 with sealed inner and outer circumferential surfaces 55 and 57 respectively.
  • the disc 14 which is attached to the wheel hub 16 is in the form of an annular plate and, in this embodiment, has attached to its opposite surfaces 18 and 20 a plurality of friction pads 22.
  • the friction pads 22 are of generally conventional construction comprising a backing plate 56 and a bonded layer of friction material 58.
  • the pads 22 are also provided with a plurality of grooves 60 on their surface 62. Each groove 60 opens at its opposite ends onto an edge 64 of its corresponding pads 22.
  • the grooves 60 assist in channeling oil in the wet brake system 10 from between the pads 22 and the stators 24. Ideally, the grooves 60 follow a spiroidal path.
  • grooves may be formed on the surfaces 26a and 26b of the stators 24a and 24b. These grooves would extend between radially inner and outer edges of each stator 24a and 24b and again provide a channeling effect for the oil within the wet brake system. In yet a further variation, such grooves may be provided on both the surfaces 26a and 26b and the surface 62 of the friction pads 22.
  • the housing 12 is formed of two annular shells 66 that are fastened together by bolts. Each shell 66 includes recesses 68 defining cylinders for housing the pistons 34. Hydraulic brake fluid inlets 70 are formed in each shell
  • Each shell 66 leading to the recesses 68 to supply hydraulic fluid for exerting pressure on the pistons 34 to activate the brakes.
  • Each shell 66 is also formed with a central hole
  • the housing 12 is similar to a conventional housing of a wet brake system previously designed by the Applicant but has been provided with an annular spacer 72 located between the shells 66.
  • the housing 12 is coupled to an axle casing (not shown) of a vehicle with the hub 16 attached to an axle disposed in the axle casing and fastened by bolts to the disc 14.
  • a wheel (not shown) is attached to ' wheel studs (not shown) projecting from the hub on an opposite side of the housing 12.
  • a small volume of lubricating liquid such as oil is held within the housing.
  • the volume of lubricating liquid within the housing 10 is arranged so that a portion of the disc 14 passes through the oil as it rotates. This oil provides lubrication between the discs 14 and the stators 24.
  • a supply of cooling fluid is coupled to the fluid inlet 28 and outlet 30 of the stators 24.
  • This fluid flows through the fluid flow paths 32 and through an associated cooling circuit (not shown) which may comprise a pump, a reservoir of cooling fluid and a heat exchanger. Heat generated by the engagement of the stators 24 with the disc 14 during the operation of the brake is transferred by thermal conduction to the cooling fluid and then dissipated through the cooling circuit.
  • an associated cooling circuit (not shown) which may comprise a pump, a reservoir of cooling fluid and a heat exchanger. Heat generated by the engagement of the stators 24 with the disc 14 during the operation of the brake is transferred by thermal conduction to the cooling fluid and then dissipated through the cooling circuit.
  • the wet brake system may comprise a plurality of co-axially arranged discs 14 with intervening stators 24 where the discs 14 are slidably mounted but rotatably coupled to the hub whereby the pistons 34 are able to effectively press the stators 24 against the friction pads 22 of each of the discs 14.
  • This in effect provides a multi-disc braking system.
  • the present embodiment depicts a pair of diametrically opposed pistons 34 acting on each stator 24. However a greater number of pistons may be provided for each shell 66 so as to act on the stators 24 at three or more spaced apart locations .

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

Abstract

L'invention concerne un système de frein à disque humide refroidi par fluide (10) qui comprend un carter étanche (12) contenant un volume d'huile lubrifiante, un disque (14) disposé dans le carter (12) et conçu pour être fixé sur un corps rotatif, tel qu'un moyeu de roue (16), et un ou plusieurs stators (24). Ces stators (24), qui sont fixés rotatifs mais montés coulissants dans le carter (12), peuvent être mis en contact avec les surfaces de freinage respectives (26) des disques au moyen de pistons de frein classiques (34). Les stators sont munis d'un orifice d'admission de fluide (28), d'un orifice d'évacuation de fluide (30) et d'une ou plusieurs voies d'écoulement fluide (32) s'étendant entre l'orifice d'admission de fluide (28) et l'orifice d'évacuation de fluide (30) à travers lesquels coule un fluide de refroidissement.
PCT/AU2004/000756 2003-06-06 2004-06-04 Systeme de frein a disque humide refroidi par fluide WO2004109143A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU2004245580A AU2004245580B2 (en) 2003-06-06 2004-06-04 Fluid cooled wet brake system
CA002527738A CA2527738A1 (fr) 2003-06-06 2004-06-04 Systeme de frein a disque humide refroidi par fluide
US11/526,066 US20080047786A1 (en) 2003-06-06 2006-09-22 Fluid cooled wet brake system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2003902857A AU2003902857A0 (en) 2003-06-06 2003-06-06 Fluid cooled wet brake system
AU2003902857 2003-06-06

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US10559363 A-371-Of-International 2004-06-04
US11/526,066 Continuation US20080047786A1 (en) 2003-06-06 2006-09-22 Fluid cooled wet brake system

Publications (1)

Publication Number Publication Date
WO2004109143A1 true WO2004109143A1 (fr) 2004-12-16

Family

ID=31953898

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU2004/000756 WO2004109143A1 (fr) 2003-06-06 2004-06-04 Systeme de frein a disque humide refroidi par fluide

Country Status (5)

Country Link
CN (1) CN100575734C (fr)
AU (1) AU2003902857A0 (fr)
CA (1) CA2527738A1 (fr)
WO (1) WO2004109143A1 (fr)
ZA (1) ZA200509377B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014176629A1 (fr) * 2013-04-29 2014-11-06 Advanced Braking Pty Ltd Système de frein à disque

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105299106B (zh) * 2015-12-05 2019-02-15 重庆元创汽车整线集成有限公司 带冷却通道的定钳盘式制动器
CN106246772B (zh) * 2016-08-11 2019-03-01 恒大法拉第未来智能汽车（广东）有限公司 一种冷却方法以及制动装置、车辆

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3022867A (en) * 1958-05-20 1962-02-27 American Steel Foundries Liquid cooled disk brake arrangement
US3915262A (en) * 1970-08-07 1975-10-28 Hermann Klaue Liquid cooled disc brake
US3999634A (en) * 1974-01-14 1976-12-28 Howell Industries, Inc. Pneumatic actuation for disc brake assemblies
US4508200A (en) * 1982-03-10 1985-04-02 Socimi, S.P.A. High performance disc brake
US4815573A (en) * 1986-10-02 1989-03-28 Akebono Brake Industry Co., Ltd Liquid-cooled disc brake
WO2002010606A1 (fr) * 2000-08-01 2002-02-07 Safe Effect Technologies International Limited Systeme de frein a disque humide

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3022867A (en) * 1958-05-20 1962-02-27 American Steel Foundries Liquid cooled disk brake arrangement
US3915262A (en) * 1970-08-07 1975-10-28 Hermann Klaue Liquid cooled disc brake
US3999634A (en) * 1974-01-14 1976-12-28 Howell Industries, Inc. Pneumatic actuation for disc brake assemblies
US4508200A (en) * 1982-03-10 1985-04-02 Socimi, S.P.A. High performance disc brake
US4815573A (en) * 1986-10-02 1989-03-28 Akebono Brake Industry Co., Ltd Liquid-cooled disc brake
WO2002010606A1 (fr) * 2000-08-01 2002-02-07 Safe Effect Technologies International Limited Systeme de frein a disque humide

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014176629A1 (fr) * 2013-04-29 2014-11-06 Advanced Braking Pty Ltd Système de frein à disque

Also Published As

Publication number Publication date
CN100575734C (zh) 2009-12-30
ZA200509377B (en) 2008-05-28
AU2003902857A0 (en) 2003-06-26
CA2527738A1 (fr) 2004-12-16
CN1802520A (zh) 2006-07-12

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