DISC BRAKE ASSEMBLY CONTAINING SPLIT DISCS

Abstract: A split disc for a brake (10) or clutch in which split discs (37, 38) are positioned for frictional engagement with full width discs (42, 43, 44). Noise reduction is provided by damping through contact friction between the split disc members (45, 46) of the split discs (37, 38). Thermal effectiveness of the discs (37, 38) is preserved by making the split disc members (45, 46) of the same thickness. Resonance of the brake (10) is reduced by splitting only the discs (37, 38) of the stator which will stagger the natural frequency of adjacent parts with little or no thermal penalty.

Description: DISC BRAKE ASSEMBLY CONTAINING SPLIT -DISCS BACKGROUND OF THE INVENTION This invention relates to disc type brakes or clutches and particularly to the arrangement of the discs of the rotor and stator„ With high performance brakes and especially disc brakes having axially integral one-piece discs objectionably shrill high frequency noise is caused by friction forces generated on the disc faces and vibrating the discs. The only damping is internal material hysteresis which -is not sufficient to subdue the vibrations and noise„ This is a serious problem because it occurs in brakes utiliz¬ ing discs of carbon composite friction material which are highly effective and desirable except for the noise. SUMMARY OF THE INVENTION According to this invention the noise produced is reduced by damping through splitting of some of the discs into two or more disc members a With the split discs the friction forces on a single disc are no longer added but act to excite separate split disc members so that the response is added 0 Because the excitation is different instantaneously and locally on each disc the response is different and micro-scale relative motion exists at the interface between the disc members of the split disc. This relative motion is resisted by the contact friction between the adjacent disc members and constitutes a damping force inhibiting the vibration of either disc member. The damping is effectively increased by adding the friction damping at the interface between the split disc members to the inherent internal damping of the disc material. By selecting an interface so that both halves of the split disc have the same thickness there is little or no thermal effectiveness penalty. The resonance of the brake assembly may also be reduced by combining the split discs with the axially integral discs. At the same time an optimum heat sink is provided by balancing and ma i iz^lϊφ'UREΛ(/ GMPΪ ■ WIPO the thermal diffusivity and heat capacitance of the discs in the rotors and stator. This is done in a convenient manner because all the discs are of the same material arid nearly the same thickness. Excluding the split discs from either the discs of the stator or the discs of the rotor staggers the natural frequency of adjacent parts with littl or no thermal penalty 0 The accompanying drawings show a preferred form made in accordance with and embodying this invention and which is representative of how this invention may be practiced. BRIEF DESCRIPTION OF THE DRAWINGS In the drawings: Fig. 1 is a fragmentary diametrical cross- sectional view of a brake embodying the invention (shown in solid lines) mounted for operation on a typical air¬ craft wheel installation with the wheel being represented by chain-dotted lines. Fig. 2 is a fragmentary view in perspective of one of the split discs showing one of the connecting clips in expanded relationship„ DETAILED DESCRIPTION Referring to Fig. 1 a friction mechanism such as the brake 10 is shown mounted on a generally cylindrical wheel 11 having matching wheel sections 12 and 13. Each of the wheel sections 12 and 13 has rim members 14 and 15, web members 16 and 17, and hub members 18 and 19 respec¬ tively. The wheel sections 12 and 13 may be fastened together by bolts (not shown) disposed in aligned holes » of the web members 16 and 17. The hub members 18 and 19 are supported for rotation on bearings 22 mounted on a nonrotatable axle member 23 0 Outboard of the wheel 11 or away from the web member 16, a torque flange 24 is mounted on a boss 25 of the axle member 23. The torque flange 24 supports a torque frame 26 seated on the boss 25 and extending radially OMP outward from the axle member 23. Inboard of the torque flange 24 and also seated on the boss 25 of the axle member 23 is a torque tube 27 extending inboard towards the web member 16 and within the space between the rim member 14 and hub member 18. The torque flange 24, torque frame 26 and torque tube 27 may be fastened together by suitable means such as bolts 28 at circumferentially spaced-apart positions around the flange. At the inboard end of the torque tube 27 an annular radially extending reaction plate member 29 may be fastened to the torque tube by suitable means such as bolts (not shown). ' On the radially outward surface of the torque tube 27 axially extending spline members 32 are disposed at circumferentially spaced-apart positions around the torque tube. Key members 33 are positioned adjacent the rim member 14 and have lugs 34 at their inboard ends which are disposed in slots in wheel web member 16. The outboard ends are fastened by bolts 35 to the wheel rim member 1 . The key members 33 extend generally in an axial direction and are positioned at circumferentially spaced-apart positions around the wheel 11. Spline members 32 support nonrotatable discs 36, 37, 38 and 39 which have slotted openings at circumferen- tially spaced-apart positions around the inner periphery and constitute the stator of the brake 10. Rota able discs 42, 43 and 44 have openings at the outer periphery for engaging the key members 33 and form the rotor of the brake 10. All of the nonrotatable discs 36 through 39 and rotatable discs 42 through 44 are of a suitable brake material for withstanding high temperatures and providing a heat sink and in this embodiment the discs are of a carbon composite friction material a As shown in Fig. 1 the rotatable disc 42 is positioned between nonrotatable discs 36 and 37, the rotatable disc 43 is positioned between nonrotatable discs 37 and 38, and rotatable disc 44 is positioned between nonrotatable discs 38 and 39 * The end nonrotatable discs 36 and 39 have a thickness Tl which is one-half the thickness T2 of the other stationary discs 37 and 38 and the ro¬ tatable discs 42, 43 and 44. Referring to Fig. 2 nonrotatable disc 37 is shown and the following description will also apply to 5 nonrotatable disc 38 which is identical to nonrotatable disc 37. Nonrotatable disc 37 is split into two disc members 45 and 46. Although a nonrotatable disc 37 may be split into more than two disc members it is prefer¬ able to have only two disc members with the same thick- 10 . ness Tl which is half the thickness T2 of the disc 37. Interposed between the disc members 45 and 46 is a sep¬ arating sheet member 47 of graphite foil or other ' simil material to prevent melting or welding together of the two disc members under the high temperatures and press- 15 ures of operation. The disc members 45 and 46 have aligned slotted openings 48 at circumferentially spaced apart positions around the inner periphery of the disc members. The rotatable discs 42, 43 and 44 have simila openings at circumferentially spaced-apart positions 20 around the outer periphery of the discs. It is preferred that a suitable connecting means such as wear-resistant bearing members 49 are dis posed in the openings 48 for transmitting or resisting transmission of rotational torque. The bearing members 25 49 have lugs 52 extending circumferentially along the outer surfaces of the discs 37 and 38. The lugs 52 may have holes 53 which in the installed position of the bearing members 49 are in alignment with holes 54 in th disc members 45 and 46. Rivets 55 may be positioned in 30 the holes 53 and 54 to hold the bearing members 49 in place and also connect the disc members 45 and 46. Sim lar bearing members, lugs and rivets may be used in the openings of the rotatable discs 42, 43 and 44 as well a in openings in nonrotatable end discs 36 and 39 for sli 35 ing engagement on the key members 33 and on the spline members 32. As stated, use of a connecting means such as bearing members 49 is preferred but is, however, not TR! OM absolutely necessary- In: certain situations where bear¬ ing members such as 49 are not necessary, they may not be used and thus, there would be no connecting means be¬ tween the disc members of each disc. . The brake actuating mechanism consists of hy¬ draulic piston and cylinder assemblies 56 disposed at spaced-apart positions around the brake 10. Each of these piston and cylinder assemblies 56 is mounted in a cylindrical housing 57 of the torque frame 26. A piston rod 58 of each of the piston and cylinder assemblies 56 engages a retractor plate 59 disposed between the non¬ rotatable disc 36 and the torque frame 26. A suitable retractor mechanism of a type well known to those skill¬ ed in the art may also be mounted at spaced-apart posi- tions around the torque frame 26 and have rods fastened to the retractor plate 59 with automatic adjusting or wear compensating mechanism. In operation, hydraulic fluid from a source of fluid pressure not shown is communicated to the piston and cylinder assemblies 56 causing the piston rod 58 to displace the retractor plate 59 towards the right as shown in Fig. 1 and thereby slide the outboard nonrotat¬ able disc 36 along the spline members 32 and into engage¬ ment with the rotatable disc 42. In the same manner the rotatable disc 42 slides along the key members 33 into engagement with nonrotatable disc 37 until eventually all of the discs are in engagement and under pressure one against the other and against the reaction plate member 29. During the period of engagement the friction forces on the split nonrotatable discs 37 and 38 cause virbration of the disc members 45 and 46 however because the excitation is different instantaneously and locally on each disc member the response is different and icro- scale relative motion exists at the inner face between the disc members. This ' relative motion is resisted by the contact friction between the rotatable disc 42, 43 and 44 and the nonrotatable discs 36, 37, 38 and 39 and constitutes a damping force inhibiting the vibration of either disc members 45 or 46. Damping and reduction in noise can be further increased by splitting the nonrotatable discs 37 and 38 into more than two disc members however this will de¬ crease the effectiveness of the discs 37 and 38 as heat sinks. By providing the interface between the disc members 45 and 46 at the midpoint of the discs 37 and 38 little or no thermal effectiveness penalty is realized. By alternating relatively thin discs with the relatively thick discs there is a reduction in noise ob¬ tained because the natural frequencies of adjacent parts are staggered and this reduces the reasonance of the brake. A similar effect can be obtained by changing the material of the adjacent parts. Both of these expedient however decrease the effectiveness of the assembly as a heat sink. The optimum heat sink requires 'balancing and maximizing the thermal diffusivity and heat capacitance of the rotors and stators. This is most effectively done when all discs of the rotors and stators are of the same material and nearly the same thickness. By split¬ ting the discs 37 and 38 of the stator this staggers the natural frequency of the adjacent discs with little or no thermal penalty. It is also contemplated that in¬ stead of splitting the discs 37 and 38 of the stator ro¬ tatable discs 42, 43 and 44 may be split. Also all of the discs of the stator or rotor may be split to lower the natural frequencies but this will not reduce the re¬ sonance of the brake assembly 10. With the construction shown in the drawings and described hereinabove noise reduction is obtained without sacrificing thermal effect iveness of the brake 10.

Claims: CLAIMS 1. A disc for a brake or clutch having para¬ llel faces for engagement with opposing faces of an as¬ sociated brake or clutch member, said disc being split into at least two disc members. 2. A disc for a brake or clutch according to claim 1 wherein said disc members have the same thickness. 3. A disc for a brake or clutch according to claim 1 wherein there are only two disc members. 4. A disc for a brake or clutch according to claim 4 wherein said two disc members have the same thickness. 5. A disc for a brake or clutch according to claim 1 wherein a separating sheet Tnember is interposed between said adjacent disc members to maintain their separate integrity. 6. A disc for -a brake or clutch according to Claim 1 wherein said disc members are of a carbon com¬ posite friction material. 7. The disc for a brake or clutch according to Claim 1 further comprising connecting means located at circumferentially spaced-apart positions at the inner or outer periphery of said disc members for forming said disc members together. 8. A disc for a brake or clutch according to claim 7 wherein said disc members have slotted openings at the inner or outer periphery, said slotted openings being located at circumferentially spaced-apart positions around said disc members and said connecting means in- eluding wear resistant bearing members disposed in said openings for transmitting or resisting the transmission of rotational torque. 9. A disc for a brake or clutch according to claim 8 wherein said openings are at the inner periphery of said disc members. OMPI 10. A friction mechanism such as a brake or clutch having spaced-apart nonrotatable discs, rotatab discs positioned adjacent to said nonrotatable discs f frictional engagement with said nonrotatable discs, at least one of said discs being split into at least two disc members. 11. A friction mechanism according to claim further comprising connecting means located at circumf entially spaced-apart positions at the inner or outer periphery of said disc members for joining said disc members together. 12. A friction mechanism according to claim wherein said discs have slotted openings at the inner periphery of said nonrotatable discs and at the outer periphery cf said rotatable discs, said slotted openin being located at circumferentially spaced-apart positi around the discs and said connecting means includes we resistant bearing members disposed in said openings fo transmitting or resisting the transmission of rotation torque and for joining together said disc members of t split disc. 13. A friction mechanism according to claim wherein said disc which is split into at least two dis members is one of said nonrotatable discs. 14. A friction mechanism according to Claim wherein a plurality of said nonrotatable discs and sai rotatable discs have the same thickness. 15. A friction mechanism according to Claim wherein said nonrotatable discs are all split and have the same thickness except for end discs having half th thickness of said other nonrotatable discs. 16. A friction mechanism according to Claim wherein said nonrotatable and said rotatable discs are the same material. 17. A friction mechanism according to Claim wherein said rotatable and nonrotatable discs are of a carbon composite friction material. 18. A friction mechanism according to Claim 15 wherein said nonrotatable discs are split into disc members of equal thickness. 19. A friction mechanism according to Claim 10 wherein a separating sheet member is interposed between said disc members. OMPI_

Inventors: ENRIGHT J
Applicants: GOODRICH CO B F
Application year: 1979
Main classification: F16D65
IPC codes: F16D65