CA1074715A

CA1074715A - Brake assembly

Info

Publication number: CA1074715A
Application number: CA301,986A
Authority: CA
Inventors: William J. Williams
Original assignee: Rockwell International Corp
Current assignee: Boeing North American Inc
Priority date: 1977-04-27
Filing date: 1978-04-26
Publication date: 1980-04-01
Also published as: JPS53134171A; AU3472178A; FR2389040A1; MX5394E; NL190563C; GB1600535A; MX7594E; NL190563B; BR7802603A; DE2818682A1; JPS6143578B2; FR2389040B1; DE2818682C2; IT1094112B; IT7822572A0; AU525102B2; NL7803692A

Abstract

BRAKE ASSEMBLY
Abstract of the Disclosure A brake assembly including a pair of brake shoes having adjacent ends pivotally mounted to a support and an actuator disposed between the ends of the brake shoes. The brake shoe webs are recessed at one end to engage a fixed anchor pin. The recess provides an arcuate bearing surface adapted to bear against a portion of the pin and permit pivoting movement of the brake shoe about the pin as the brake is actuated and released. The recess is also so oriented relative to the pin that the recess abuts the pin and prevents the brake shoe from moving away from the anchor pin. The brake assembly also includes an anchor pin having axially spaced cylindrical bearing areas adapted to radially, slidably receive the open ended recesses of a dual web brake shoe and a pair of oppositely facing surfaces extending radially outward at axially spaced locations on the pin to abut the brake shoe webs and prevent the anchor pin from being axially displaced from the support.

Description

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BACKGROUND OF TIIE INVENTION
Field of the Invention. The present invention is directed to certain improvements in vehicle brake mechanisms and, more specifically, to a brake shoe and an anchor pin for a vehicle brake assembly.
Description of the Prior Art. The invention is particularly useful in a rotary cam actuated brake assembly which ;ncludes a pair of brake shoes having adjacent ends pivotally mounted to a support and a rotatable actuating cam disposed between the other ends of the brake shoes. Rotary movement of the cam causes each of the brake shoes to pivot outwardly about ;ts pivot or anchor pin to contact the inwardly facing friction surface of the brake drum. This type of brake assemb.ly is used for heavy duty brake applications which may employ a dual or a single web brake shoe. The brake shoes may be cast or fabricated. The brake shoes may also carry a roller type cam follower on the ends adjacent the actuating cam. The opposite ;
adjacent ends of the brake shoes may be mounted for pivoting move-ment about a single anchor pin as disclosed in United States Patent No. 3,398,814 or each shoe may be pivo~ally mounted for movement about one of a pair of spaced anchor pins as disclosed in Patent No.
3~114J~37~
Dual web brake shoes for the brake assemblies employing a pair of spaced anchor pins are provided with axially aligned, laterally extending bores in each of the webs at the end of the ~74~15 shoe to be pivotally mounted to the support. The brake shoes are mounted to the assembly by aligning the web bores on opposite sides of a bore through a boss formed on the brake support or spider and inserting a pin axially through the spider bore and the coaxial brake shoe bores. The pin, generally referred to as an anchor pin, may be press fit to the boss or locked against rotation by a set screw or other means. Snap rings may be provided to the axially extending ends of the pin to prevent substantial axial displacement of the anchor pin relative to the support. The foregoing arrangement fixes the brake shoe against substantial movement relative to the support except for the desired pivoting movement about the anchor pin. In this type of brake assembly the anchor pin must be withdrawn from the spider bore when it becomes necessary to remove the brake shoes for the purpose of replacing or relining the same.
- This is not necessary in brake assemblies of the type where the brake shoes are mounted for pivoting movement about a single anchor pin. In that type of assembly the adjacent ends of -the brake shoe webs are each recessed to provide arcuate bearing surfaces usually less than 180 in arc, which are seated on opposite sides o~ the anchor pin by a radially direc~ed movement relative to the pin. The open ended recesses provided to the brake shoe ends permit assembly to and disassembly from the anchor pin without moving the anchor pin relative to the spider.
Although this arrangement provides for ease of assembly and disassembly, the brake shoes are not positively secured to the ; anchor pin and may become self-actuating. That is, when the ` brake assembly is actuated, the cam causes the brake shoes to pivot about the anchor pin to bring the friction lining padæ into contact with the brake drum and thereby inhibit rotation of the brake drum and tbe wheel to which it is attached. The friction force between the brake drum and the linings secured to the brake .

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shoes tends to ~raw the linings into further contact with the brake drum and thereby increase the magnitude of the friction force. The effect the friction force will have on the linings depends upon the direction of rotation of the brake drum.
The friction force between the drum and the lining secured to one of the brake shoes will be effective in the same general direction as the force applied by the cam actuator and will compliment the brake actuating force. The friction force between the drum and the lining secured to the other brake shoe will be opposite to the direction of the force applied by the rotatable cam actuator. The friction force at the circumference of that brake shoe will tend to move the brake shoe away from the anchor pin and toward the actuating cam at the other end of the shoe.
Under static conditions there is virtually no space available to accommodate any movement of the brake shoe other than the intended pivotal movement into contact with the friction surface of the brake drum. However, the brake assembly distorts under dynamiG braking conditions. The system pressure and temperature generated during braking cause the brake shoes and the brake drum to expand radially in those areas where the pressure and temperature increase is the greatest. Drum type brake assemblies which are normally depicted as comprising a plurality of brake shoes with friction lined tables of generally cylindrical curvature and closely surrounded by a cylindrically curved friction surface of a brake drum under static conditions become elliptical or oblate under dynamic braking conditions. In a rotary cam actuated brake assembly the brake drums and brake shoes expand radially at about the mid-point of the brake shoes and aford additional clearance for the anchor ends of the brake shoes to move away from the anchor pins if the brake shoe webs are not secured against such movement. Movement of the brake shoe .. . .

~37~q~5 away from the anchor pin causes undesirable noise and chatter as well as unnecessarily rapid wear of the lining on the brake shoe most often subject to this type of "self-actuation".
Although the components of the brake assembly could be made more massive to produce an assembly which is less susceptible to distortion under dynamic braking conditions, such an assembly would be economically unfeasible because of the additional metal required in the manufacturing process and the mass added to the weight of the vehicle. The economics of manufacture and vehicle operation thus dictate that the state of the art rotary cam actuated brake assembly is both satisfactory and reliable and should be improved wherever possible to enhance its operation and servicability.
SUMMARY OF THE INVENTION .
The present invention providcs an anchor pin for a vehicle brake assembly comprising an elongate pin having axially spaced cylindrical bearing areas adapted to radially, slidably rece;ve an open ended recess of a dual web brake shoe and a pair of oppositely facing surfaces integrally formed with said anchor pin and extending radially outward at axially spaced locations on said pin to prevent ~0 substantial axial movement of said anchor pin in either direction relative to said dual web brake shoe.
The invention and the advantages offered thereby will become apparent from the following detailed description of the embodiments shown by the accompany drawings.

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. , , ' '' . . ! ' ' l ' ' ~ ' ' ~7~7~5 ~RrEF DESCRIPTION OF THE DRAWINGS
In the drawings wherein like reference numerals refer to like parts:
Figure 1 is a side elevation, partly in section of a brake assembly;
Figure 2 is a view, partly in section, taken along line 2-2 of Figure l;
Figure 3 is a fragmentary view showing part of the brake shoe and brake spider of the brake assembly shown by Figure l;
1~ Figure 4 is a fragmentary view showing an alternate embodiment;
Figure 5 is a bottom view of the embodiment of Figure 4;
Figure 6 is a fragmentary view, partly in section, showing an alternate means for pivotally mounting the brake shoes of Figure l;

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~74~15 Figure 7 is a perspective view showing the anchor pin of Figure 6;
Figure 8 is a view similar to Figure 6 but showing a means of pivotally mounting the brake shoes of Figure 1 to a different type of support; and Figure 9 is a perspective view showing the anchor pin of Figure 8.

DESCRIPTION OF THE INVENTION
With reference to the drawings, there is shown a cam actuated brake assembly generally designated by the numeral 10.
The brake assembly 10 is supported by a spider 11 rigid with a vehicle axle housing 12. The brake assembly 10 includes a pair of brake shoes 14 each of which is pivotally mounted at one end to an anchor pin 15 carried by the spider 11. The anchor pins 15 are each carried in a cylindrical bore 16 provided through bosses 180 As best shown by Figure 2, the bosses 18 are formed as depending integral parts of the spider 11 and are axially offset from the upper portion of the spider 11. The offset permits the bosses 18 to be located between the dual webs of the brake shoes 14.
A cam 19 is mounted for rotary movement between the adjacent ends of the brake shoes 14 opposite from the anchor pins 15. The brake shoes 14 are each provided with a roller type cam follower 22. The cam is non rotatably secured to a cam shaft 20 mounted to tbe spider for rotary movemen~ in a bearing 21. Th~
cam shaft is rotated by means not shown to rock the cam 19 in a closkwise direction through an arc in the range of 10 to 30.
The cam 19 provides an outwardly directed force to the rollers 22 and the brake shoes 14 which causes the brake shoes ~o pivot about the anchor pins 15. This movement forces the friction lining pads 24 into contact with the inwardly facing friction surface 26 of a brake drum 25 secured by conventional means 23 to a wheel 27 rotatably mounted by hub 29 to a spindle at the outer end of axle 16~7~5 housing 12. When the brakes are released the brake shoes 14 and the friction lining pads 24 are withdrawn from contact with the brake drum surface 26 by a return spring 28 secured at its opposite ends to the brake shoe webs.
The brake shoes 14 are dual web fabricated brake shoes.
That is, each brake shoe includes a pair of axially spaced webs 31 secured to a table 32. The webs 31 are flat in a radial direction and curved in a longitudinal or circumferential direction. The brake shoe table 32 is curved in the circumferential direction and the webs 31 are welded in parallel relation along the interior curved portion of the table. This provides a generally rigid assembly of component parts to which the friction lining pads 24 may be secured by rivets or by chemical bonding.
Each of the brake shoe webs 31 is provided with an open recess 34 at the end opposite the ca~ follower 22. The recess 34 is in the form of a slot which includes an inner arcuate bearing surface 35 and a mouth formed by integral brake shoe portions 36, 38 whicb extend tangentially outward from the opposite ends of the arcuate bearing surface 35. The bearing surface 35 is a semi-circular bearing surface adapted to engage a complementary arcuate surface 17 of the generally cylindrical end portion 13 of anchor pin 15. The bearing surface 35 is comprised of an upper portion 37 and a lower portion 39. The recess 34 is canted so the upper and lower portions 37 and 39 of the bearing surface 35 are disposed to enyage the complementary arcuate surface 17 at the botton of pin 15 on both sides of a radial plane passing through the center of anchor pin 15 and the axis of rotation of the wheel 27 carried by axle housing 12. The plane is represented by the line A in Figure 3 which passes through the center of anchor pin lS and the longitudinal center of axle housing 12 which is coaxial with the axis of rotation of brake drum 25 and the wheel 27 to which the brake drum is secured.

~7~7~5 With reference to Figures 1 and 3, the outer end of the lower portion 39 of arcuate bearing surface 35 and the web portion 38 of the brake shoe 31 shown to the left in the drawings are disposed to bear against a por tion of the complementary arcuate surface 17 to the right of the plane represented by the line A. When the brake assembly 10 is actuated with the wheel and brake drum 25 rotating in a clockwise direction as indicated by the arrow in Figure l, the friction developed between the pads 24 and surface 26 of brake drum 25 will develop a circumferentially directed force tending to move both of the brake shoes 31 in a clockwise direction. The circumferentially directed force between the brake drum 25 and the friction linings 24 secured ~o the brake shoe 31 shown to the right in Figure 1 will tend to move that brake shoe in the direction of its anchor pin 15 and thus compliment the brake actuating force applied by cam 19. The circumferentially directed force developed between the brake drum 25 and the friction linings 24 secured to the brake shoe 31 shown to the left in Figure l will be opposite to the force applied by the cam 19 and, if that brake shoe were not restrained, the circumferentially directed force would move the brake shoe away from the anchor pin 15 in a clockwise direction toward the other end, that is, the cam follower end of the brake shoe. The canted recess 34 of the brake shoe 31 prevents such movement. A portion o the complementary arcuate surface 17 of pin 15 bears against the lower end surface 35 to the right of the plane represented by line A and prevents the brake shoe from moving away or becoming disassociated with the anchor pin.
The width D of the mouth portion o recess 34 and the diameter of the inner arcuate bearing surface 35 are selected to as to permit the brake shoes to be slidably engaged with the ends of the anchor pin 15 projecting from opposite sides of the spider boss 18. This arrangement provides for ease of assembly and . . . :

47 iL5 disassembly while the lower portion 39 of the recess and the web portion 38 are hooked around a portion of the anchor pin 15 remote from the primary bearing portion. The lower end portion 39 of the recess and the web portion 38 are thus oriented to abut that remote portion of the anchor pin 15 and prevent the brake shoe moving away from the anchor pin as the brake shoes become self-actuating. Due to the clearance provided for ease of assembly, the brake shoe web will move a limited distance until the hooked end of the web abuts the anchor pin, but once the recess abuts the pin it will prevent further movement of the brake shoe in response to a force tending to move the brake shoe away from the anchor pin.
Although for ease of manufacture and assembly it is preferred to utilize a semi-circular inner arcuate bearing surface 35, the bearing surface of recess 34 may be less than 180 of arc from end to end. The recess 34 or slotted ends of the brake shoes 31 are preferable canted at an angle between about 5 and 30 relative to the plane represented by the line B in Figure 3. The line B represents a plane passing through the center of anchor pin lS and parallel to the vertical axis of the brake assembly which passes through the center of the rotary cam as shown in Figures 1-3. With an inner arcuate bearing surface of 180 this disposes 5 to 30 of the arcuate bearing surface 35 at the lower end portion 39 on the right or remote side of the plane represented by the line B as shown in Figure 3.
The amount of extension beyond the plane passing throuqh the center of the anchor pin and the axis of rotation of the wheel required to retain the recessed end of the brake shoe web on the anchor pin is dependent on the size of the brake and the location of the anchor pins relative to the axis of rotation and the diameter of the friction surface of the brake drum. The orientation of the recess as described above has proven - - - . ~ . . . . . . .

~7a~7~5 satisfactory on a 16-1/2 inch nominal diameter brake assembly having a pair of anchor pins spaced 2-1/2 inches apart on a line 6-3/4 inches below the horiæontal center line and having a 1 inch diameter recess bearing surface. Although the orientation may differ for other brake assemblies, adequate retention can be obtained so long as the lower end 39, 38 of the recess extends beyond the plane represented by the line B in Figure 3. In the embodiment shown by Figures 1-3 the lower end portion 39 of the recess 34 extends about 20 beyond the right side of the plane represented by the line B while the web portion 39 which extends tangentially from the lower end portion 39 of reces~ 34 extends a substantial distance, about 1/~ inch, beyond the lower end portion 39.
Although the recesses 34 may be of the same thickness as the brake shoe webs 31, it is preferred to provide a yreater surface area for bearing against the anchor pin 15. The area of the arcuate bearing surface 35 may be increased by providing a shoulder 40 around the recess 34. This may be accommodated by welding a U-shaped element to the surface of the web 31.
During assembly the anchor pins 15 are fitted to the bores 16 of the spider bosses 18. The brake shoes 31 are mounted to the spider by sliding the recesses 34 in a generally radially direction over the cylindrical ends 13 of the anchor pins 15 extending from the opposite sides of the spider bosse~ 18. The webs 31 of each brake shoe may be through punched with laterally aligned holes 41. A pin 42 is inserted through the laterally aligned holes 41 of each brake shoe 14 and the opposite ends of a retention spring 44 are hooked around each respective pin 42 The retention spring 44 helps spring 28 urge the arcuate bearing surfaces 35 provided at the recessed ends of the brake shoes 14 into contact with the anchor pins 15.

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A pair of snap rings 45 are seated in grooves 46 provided adjacent the opposite ends of the anchor pins 15 to prevent axial movement of the brake shoe webs 31 ~elative to each anchor pin 15.
The remaining components of the brake assembly 10 as shown by Figure 1 and the brake drum 25 are added in conventional manner.
Figures 4 and 5 show an alternate embodiment of the present invention where a pair o~ brake shoes 51 having open ended recesses 52 are pivotally mounted to a single anchor pin 54. In this embodiment the brake shoe tables 55 are provided with friction lining material 56 and the recessed end of one of the webs 58 of each brake shoe is axially offset to seat on the pin 54 internally adjacent the recessed end of the web 59 of the other brake shoe. A similar arrangement using axially offset recessed ends may also be utilized to pivotally mount single web brake shoes on a single anchor pin.
The brake shoes of the invention thus, through the anchor pin recesses and their particular orientation relative to the anchor pins supported by the spider, provide for ease of assembly and disassembly while avoiding the self-actuating feature associated with prior art brake assemblies utilizing brake shoes having open ended anchor pin recesses.
Figure 6 shows an alternate arrangement for mounting a dual web brake shoe with each web having an open ended recess to a support boss of the type disclosed in Figures 1-3. In Figure 6 an anchor pin 60 is inserted in a bushing 61 seated in the cylindrical bore 16 of spider boss 18.
The anchor pin 60, as best shown by Figure 7, is an elongate member having a stepped cylindrical surface comprised of a cylindrical bearing surface 62 and 64 at each end and a cylindrical mounting surface 65 extending a substantial axial .
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1~'7~7~5 distance between the bearing surfaces 62 and 64. The surfaces 62, 64 are of the same diameter and are smaller than the mounting surface 65. The surfaces 62, 64 are also separated from the mounting surface by a pair of oppositely facing radially extend-ing surfaces 66 and 68.
The diameter and length of the mounting surface 65 provide a snug fit in the bushing 61 with the oppositely facing radial surfaces 66 and 68 flush with the external surfaces of the spider boss 18. The recessed ends 34 of a dual web brake shoe are radially slidably engaged or seated on the cylindrical bearing surfaces 62 and 64. As the return spring 28 and/or the retention spring is applied to the brake shoes, the cam follower ends of the brake shoes are biased toward the rotary cam and the open ended recesses are firmly seated on the bearing surfaces 62 and 64. The width D of the recesses 34 is not as large as the diameter of the moun~ing surf~ce 65. The portion of the brake shoe webs surrounding the recesses 34 thus serve as abutments which are contacted by the radially extending surfaces 66, 68 of the anchor pin and prevent substantial axial movement of the anchor pin 60 relative to the brake shoe webs 31 and thereby prevent the anchor pin 60 from being axially displaced from the bore 16.
~ igure 8 shows a further arrangement for mounting a dual web brake shoe with each web having an open ended recess to a brake assembly supportO In Figure 8 the brake support or spider is formed to provide a pair of axially spaced depending bosses 71 and 72 with a cylindrical bore 73, 74 or a pair of axially aligned cylindrical bores 73, 74 extending through said bosses.
The anchor pin 70, as best shown by Figure 9, is an elongate member having a stepped cylindrical surface comprised of a cylindrical mounting surface 76 and 77 at each end and a cylindrical bearing surface 78 extending a substantial a~ial distance between the mounting surfaces 76 and 77. The mounting 1~174715 surfaces 76, 77 are of the same diameter and are larger than the bearing surface 78. The bearing surface 78 is separated from the mounting surfaces 76, 77 by a pair of oppositely facing radially extending surfaces 79 and 80.
The diameter and length of the mounting surfaces 76 and 77 provide a snug fit in the bores 73, 74 of the axially spaced bosses 71, 72 with the radial surfaces 79 and 80 flush with the internal surfaces of the bosses 71, 72. The recessed ends 34 of a dual web brake shoe are radially, slidably engaged or seated on axially spaced bearing areas of the bearing surface 78. The return and/or retaining springs are applied to bias the brake shoes toward the rotary cam and firmly seat the recesses 34 on the anchor pin 70. As in the embodiment of Figure 8, the width D of the recesses 34 is not as large as the diame~er of the cylindrical mounting surfaces 76, 77 and the webs surrounding the recesses 34 serve as abutments contacted by the radially extending surfaces 79, 80 of the anchor pin. The brake shoe webs 31 and anchor pin surfaces 79, 80 thus interact to prevent substantial axial movement of the anchor pin 70 relative to the brake shoe webs and thereby prevent the anchor pin 70 from being axially displaced from the spaced bores 73, 74.
The anchor pins 60 and 70 both comprise an elongate pin having stepped cylindrical bearing areas for receiving the open ended recesses of a dual web brake shoe and a pair of oppositely facing surfaces extending radially outward at axially spaced locations to prevent the anchor pin from substantial movement relative to the brake shoe webs and, more importantly, to prevent the anchor pin from being axially displaced from the brake support bore. As such, the anchor pins do not require other means such as snap rings or pressure plates to secure the pins against accidental displacement from the brake support bore.

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~'7~715 When used with the open ended dual web brake shoes described in conjunction with Figures 1-3, the smaller diameter bearing surfaces of the anchor pins 60 and 70 provide a stronger web portion to hook around the anchor pin. This is beneficial due to the high stresses encountered as the anchor pin holds the hooked end of the brake shoe web against displacement under dynamic braking conditions. Increased web end strength is provided by the smaller diameter cylindrical bearing surfaces while the larger diameter cylindrical mounting surfaces of the anchor pins 60 and 70 permit the improved, open ended, dual web brake shoes to be used with brake support plates having large diameter anchor pin bores. The anchor pins 60 and 70 may thus be used with the improved open ended, dual web brake shoes as replacement parts for brake assemblies already in service and as components for new brake assemblies without changing the tooling for manufacturing the brake support plates.
The invention may also be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The foregoing description is therefore to be considered as illustrative and not restrictive, the scope of the invention being defined by the appended claims, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced thereby.

Claims

THE EMBODIMENTS OF THE INVENTION IN WHICH AN EXCLUSIVE PROPERTY OR
PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:

1. An anchor pin for a vehicle brake assembly comprising an elongate pin having axially spaced cylindrical bearing areas adapted to radially, slidably receive an open ended recess of a dual web brake shoe and a pair of oppositely facing surfaces integrally formed with said anchor pin and extending radially outward at axially spaced locations on said pin to prevent substantial axial movement of said anchor pin in either direction relative to said dual web brake shoe.

2. The anchor pin defined by claim 1 wherein said axially spaced cylindrical bearing areas are provided by a cylindrical bearing surface at each end of said anchor pin and each of said cylindrical bearing surfaces is bounded at its axially inner end by a radially extending surface of said anchor pin.

3. The anchor pin defined by claim 1 wherein said axially spaced cylindrical bearing areas are provided by a cylindrical bearing surface intermediate the ends of said anchor pin and said cylindrical bearing surface is bounded at each of its axially outer ends by a radially extending surface of said anchor pin.

4. An anchor pin for a rotary cam actuated brake assembly comprising an elongate pin having a stepped cylindrical surface including a cylindrical brake shoe bearing surface of one diameter at each end thereof and a cylindrical mounting surface of greater diameter extending a substantial axial distance between said cylindrical bearing surfaces.

5. An anchor pin for a rotary cam actuated brake assembly comprising an elongate pin having a stepped cylindrical surface including a cylindrical mounting surface of one diameter integrally formed at each end thereof and a cylindrical brake shoe bearing surface of smaller diameter extending a substantial axial distance between said cylindrical mounting surfaces.

6. In a rotary cam actuated brake assembly for a vehicle wheel comprising a support having an opening therethrough and a pair of brake shoes with each brake shoe having a pair of axially spaced webs, the combination of an elongate member having a first portion adapted to be axially inserted in said support opening and a second portion providing axially spaced cylindrical bearing areas, and an open ended recess in each web at one end of each of said brake shoes, the recesses at each of said brake shoe ends being laterally aligned with each other and the width of said recesses being large enough to radially, slidably engage said cylindrical bearing areas but less than the corresponding width of said first portion of said member to prevent said first portion of said member from moving a substantial axial distance between said webs when both of said recesses are engaged with said cylindrical bearing areas.

7. The rotary cam actuated brake assembly defined by claim 6 wherein said opening is a bore through said support and said first portion of said elongate member is a cylindrical mounting surface intermediate said cylindrical bearing areas and of greater diameter than said cylindrical bearing areas.

8. The rotary cam actuated brake assembly defined by claim 6 wherein said opening is a bore provided through axially spaced bosses on said support, said first portion of said elongate member is comprised of a pair of axially spaced cylindrical mounting surfaces seated in said bosses and said second portion of said elongate member is a cylindrical brake shoe bearing surface of a diameter less than the diameter of said axially spaced cylindrical mounting surfaces and extends between said axially spaced cylindrical mounting surfaces.

9. In a brake assembly for a vehicle wheel comprising a support, a pair of brake shoes with each brake shoe having a pair of axially spaced webs, a rotary cam actuator disposed between adjacent ends of said brake shoes, the opposite ends of said brake shoes being mounted for pivotal movement about an anchor pin carried in a cylindrical bore provided through said support and means biasing the adjacent ends of said brake shoes toward said rotary cam, the improvement comprising:
an anchor pin having a cylindrical center portion seated in said bore and a cylindrical brake shoe bearing surface at each end of said center portion, each of said cylindrical brake shoe bearing surfaces being of smaller diameter than the diameter of said center portion of said anchor pin, and an open ended recess in each web at said opposite ends of said brake shoes, the width of said recesses being adapted to radially, slidably engage said cylindrical brake shoe bearing surfaces of said anchor pin but less than the diameter of said center portion of said anchor pin, said webs being spaced to seat said recesses adjacent the axially spaced ends of said cylindrical center portion of said anchor pin to prevent the center portion of said anchor pin from being axially displaced from said bore.

10. The brake assembly defined by claim 9 wherein each of said open ended recesses is comprised of an inner arcuate bearing surface and a portion of said web extending tangentially at one end of said arcuate bearing surface and said recesses are so oriented as to pivot about said cylindrical brake shoe bearing surfaces of said anchor pin in response to an outwardly directed force applied at the other end of said brake shoe and to abut said cylindrical brake shoe bearing surfaces and prevent further movement of said brake shoe in response to a force tending to move said brake shoe away from said anchor pin.

11. In a brake assembly for a vehicle wheel comprising a support, a pair of brake shoes with each brake shoe having a pair of axially spaced webs, a rotary cam actuator disposed between adjacent ends of said brake shoes, the opposite ends of said brake shoes being mounted for pivotal movement about an anchor pin carried in a pair of axially aligned bores provided through axially spaced portions of said support and means biasing the adjacent ends of said brake shoes toward said rotary cam, the improve-ment comprising:
an anchor pin having a cylindrical mounting surface at each end thereof and a cylindrical brake shoe bearing surface intermediate said mounting surfaces, each of said cylindrical mounting surfaces being of a diameter larger than the diameter of said cylindrical brake shoe bearing surface and carried in one of said axially aligned bores, and an open ended recess in each web at said opposite ends of said brake shoes, the width of said recesses being adapted to radially slidably engage said cylindrical brake bearing surface of said anchor pin but less than the diameter of said cylindrical mounting surfaces of said anchor pin, said webs being spaced to seat said recesses adjacent said mounting surfaces to prevent said mounting surfaces from being displaced from said axially aligned bores.

12. The brake assembly defined by claim 11 wherein each of said open ended recesses is comprised of an inner arcuate bearing surface and a portion of said web extending tangentially at one end of said arcuate bearing surface and said recesses are so oriented as to pivot about said cylindrical brake shoe bearing surface of said anchor pin in response to an outwardly directed force applied to the other end of said brake shoe and to abut said cylindrical brake shoe bearing surface and prevent further movement of said brake shoe in response to a force tending to move said brake shoe away from said anchor pin.