CA2210331A1 - Stabilizer link - Google Patents
Stabilizer linkInfo
- Publication number
- CA2210331A1 CA2210331A1 CA 2210331 CA2210331A CA2210331A1 CA 2210331 A1 CA2210331 A1 CA 2210331A1 CA 2210331 CA2210331 CA 2210331 CA 2210331 A CA2210331 A CA 2210331A CA 2210331 A1 CA2210331 A1 CA 2210331A1
- Authority
- CA
- Canada
- Prior art keywords
- shaft
- bushing
- pair
- link
- retainer
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
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- 229920002635 polyurethane Polymers 0.000 claims description 12
- 239000004814 polyurethane Substances 0.000 claims description 12
- 239000000463 material Substances 0.000 claims description 10
- 230000000295 complement effect Effects 0.000 claims description 6
- 238000000034 method Methods 0.000 claims description 6
- 230000013011 mating Effects 0.000 claims description 3
- 239000000725 suspension Substances 0.000 abstract description 13
- 244000228957 Ferula foetida Species 0.000 description 18
- 230000035939 shock Effects 0.000 description 12
- 238000010276 construction Methods 0.000 description 11
- 229920001971 elastomer Polymers 0.000 description 9
- 239000002184 metal Substances 0.000 description 9
- 239000005060 rubber Substances 0.000 description 9
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- GWUSZQUVEVMBPI-UHFFFAOYSA-N nimetazepam Chemical compound N=1CC(=O)N(C)C2=CC=C([N+]([O-])=O)C=C2C=1C1=CC=CC=C1 GWUSZQUVEVMBPI-UHFFFAOYSA-N 0.000 description 5
- 229920003051 synthetic elastomer Polymers 0.000 description 5
- 239000005061 synthetic rubber Substances 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 3
- 244000261422 Lysimachia clethroides Species 0.000 description 2
- 239000004677 Nylon Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 229920001778 nylon Polymers 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 239000006096 absorbing agent Substances 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 210000000887 face Anatomy 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Vehicle Body Suspensions (AREA)
Abstract
A link for a steering and suspension assembly for a bus or other vehicle comprising a pair of shafts and a housing that is defined by a pair of cylinders that are joined together by a rod or stem. Each cylinder defines a pair of contiguous tapered bores opening in opposite directions for receiving one of the shafts. Each shaft is secured to the housing by replaceable components, namely, a pair of retainers, a pair of bushings, and a fastener secured to the other threaded end of the shaft. Each pair of bushings is matingly received within bores.
Description
STABILIZER LINK
Technical Field of the Invention The present invention relates to a stabilizer or torsion bar link that can be used to stabilize the suspension for a vehicle, such as, for 5 example, a bus or a car.
Ba~k~ound of the Invention A suspension assembly for a bus or other vehicle usually includes, among other components, a torsion bar and a connecting link. The torsion bar (which also may be called a stabilizer or sway bar) is generally 10 affixed to the vehicle frame with the link functioning as the connecting member to the axle. The torsion bar absorbs torsional loading while the link additionally must act as a shock absorber.
The link can have a generally U-shaped construction that includes a metal housing and a pair of metal shafts permanently secured to 5 the housing. The shafts are also connected to other components of the assembly, such as the axle plate (or associated part) and the torsion bar.
It is known to use rubber as an intermediary to permanently secure the shafts to the housing to add flexibility to the link so that the link is better able to absorb road shocks. To construct such a link, rubber is molded 2 o to one end of each shaft. The ends of the shaft are then inserted into the bores defined in the housing. The housing is crimped radially around each bore to permanently secure the shafts to the housing.
A disadvantage of this known link, however, is that it has a relatively short life expectancy because the rubber tends to shear or become 25 worn relatively quickly and much sooner than the rest of the components.
Thus, once the rubber shears or becomes worn, the entire link is no longer useful and must be replaced.
In an attempt to provide a more durable link, an all metal link that uses all metal ball studs has been developed. This link is undesirable 3 0 because it lacks flexibility and does not absorb road shocks as well as the other link. In addition, it has been noted as the source of suspension squeak.
As a result, the all metal link tends to transfer stress to the suspension which, over time, will shorten the life of various parts in the suspension.
What is needed is a link that is capable of effectively absorbing 5 road shocks better than the prior art links, and that is more economical than the prior art links. Such a link should include a flexible element to absorb the shocks, but should also address the problem of short life expectancy associated with the known link having a flexible element. Such a link preferably is easy to assemble. The present invention meets these desires.
10 Summaly of the Invention The present invention provides a link for a steering and suspension assembly for a bus or other vehicle. In its preferred embodiment, it includes a pair of shafts or studs, and a housing that is defined by a pair of eyes or cylinders that are joined together by a rod or stem. Each cylinder 5 defines a pair of adjoining or contiguous, tapered bores opening in opposite directions for receiving a pair of bll~hings.
Preferably, both ends of each shaft are threaded, with a distal threaded end of each shaft being secured to another component of the assembly such as the axle plate (or associated part) or torsion bar. Each shaft 20 may be readily secured to the housing by replaceable components, such as, a pair of proximal and distal retainers, a pair of bll~hings, and a fastener such as a nut secured to a proximal threaded end of the shaft. In one preferred embodiment, the proximal and distal retainers are in the form of proximal and distal retaining washers. In an alternative preferred embodiment, each 25 proximal retainer is in the form of a proximal ring that is integral or unitary with its corresponding fastener, and each distal retainer is in the form of a distal ring that is integral or unitary with its corresponding shaft.
In another alternate embodiment, the link comprises a hollow cylinder including a pair of open ends; a stem associated with the cylinder for 30 mounting the cylinder to the vehicle; a bushing configuration, a shaft, and fastening elements similar to those of the preferred embodiment; and a hollow cylindrical dowel. The dowel is associated with the shaft, and is configured to be accepted into a mounting hole on a component of the steering or suspension assembly.
The dowel of this alternate embodiment allows the link to be installed on the vehicle from the opposite side of the component to avoid possible interference with another component of the suspension or steering assemblies such as a radius rod. Also, the dowel can be configured to adapt a cylindrical shaft to a tapered mounting hole or vice-versa. The dowel may, in lo fact, have a number of configurations so that a shaft having one shape can fit into mounting holes of any shape.
The bllshings preferably are constructed of polyurethane, which has a longer life expectancy than rubber or synthetic rubber and has better shock absorbing dynamics. Polyurethane also has a relatively high degree of elasticity. Preferably, the polyurethane has a hardness of about 85 to about 95 durometers on the Shore A scale, and optimally about 90 durometers.
Alternatively, the bllching~ may be constructed of rubber or synthetic rubber that preferably has a hardness of about 70 durometers.
Each pair of bushings is received within one of the respective 20 pairs of bores defined by the cylinders. Desirably, each bushing has a first frustoconical wall with a taper that narrows toward the end of the bushing.
The ffrst frustoconical outer walls preferably complement the tapered bores.
This construction elimin~tes or reduces lateral displacement of the housing relative to the bll~hing~ and shaft. The tapers also elimin~te or reduce 25 longitudinal displacement of each bushing in the direction of its adjacent bushing.
Each bushing may also have a second frustoconical outer wall with a taper that narrows toward the other end of the bushing, which extends outside the bore. This construction tends to relieve pressure and avoid pinching of the bushing between the washers and the cylinders when the bushing is under compression during service.
Preferably, the retainers are disposed about the shafts, and abut the ends of the bnshingc that extend outside the bores. If retaining washers 5 are employed, the holes defined by the proximal and distal retaining washers preferably are different sizes.
Each retainer may have a circumferential flange angled with respect to a flat portion. The flanges of each pair of proximal and distal retainers face away from the bnshing~, which also helps to relieve pressure 0 when the bushing is under compression yet still contain the bnshings in the housings. With this construction, when the shaft is deflected from center, it causes further compression of the bn~hing.c The orientation of the retainers allows relief from this compression. The flanges also provide a surface for the bushing to "roll" against.
The fasteners may be conventional castle nuts or may otherwise be adapted to engage a cotter pin for securing the fasteners. With this embodiment, one of the threaded ends of the shaft also defines a cotter pin hole for receiving the cotter pin. This construction tends to be more reliable against shock and vibration than other alternatives, and also avoids call~ing 20 damage to the threads of the shafts. Alternatively, however, a nylon insert nut or an all metal lock nut can be used.
The preferred embodiment of the present invention provides a link that is more economical than the prior art links because its components can be easily and quickly replaced when they fail or become worn. As a 25 result, the link can be reused and does not have to be discarded when one of its components fails or becomes worn.
In this regard, cost savings likely will be appreciated most in connection with the replacement of bll~hings since they tend to have substantially shorter lives than the rest of the components of the link and also3 0 tend to be significantly less expensive than the housing and shafts. Thus, with the present invention, the bllshing~ can be continuously replaced as they become worn, thereby substantially extending the life of the link.
If desired, the link may be sold together as a fully-assembled link. Alternatively, all of the components may be sold together (e.g. the housing, retainers, bllshing~, fasteners and pins) in a container such as a box or bag as a kit, if desired. The components can then be assembled and installed on a vehicle. Thereafter, when the bllshings (or other components) become worn, new bllshings (or other components) can be obtained separately from the kit, and then can be replaced.
0 Similarly, the components that tend to be replaced more frequently can also be sold together as a kit. For example, two pairs of bllshing~, two pairs of retainers, a pair of fasteners and a pair of cotter pinsmay be sold together in a package to be used when any or all of these original (or previously replaced) components become worn. In an alternative embodiment described above, the kit may include two pairs of bll~hing~, the pair of fasteners each with unitary proximal retainers, and a pair of cotter pins. Such a kit enables quick and easy replacement of the corresponding components.
Numerous other advantages and features of the present 2 o invention will become readily apparent from the following detailed description of the invention and the embodiments thereof, from the claims and from the accompanying drawings.
Brief Description of the Drawin~c FIGURE 1 is an exploded perspective view of a link in accordance with one embodiment of the invention;
FIGURE 2 is a partial exploded and partial cross section view of a link similar to the link of FIGURE 1;
FIGURE 3 is a plan view of the side of the housing of the link of FIGURE 2, illustrating with dotted lines the inner walls of the cylinders;
FIGURE 4 is a plan view of the top of the housing of FIGURE 3;
FIGURE S is a cross section view taken along the lines S-S of FIGURE 4;
FIGURE 6 is a broken and partial cross section view of a link in accordance with a further alternative embodiment of the invention;
FIGURE 7 is a side elevational view of the shaft of the link of FIGURE 6;
FIGURE 8 is a side elevational view of an integral fastener and proximal retainer of the link of FIGURE 6;
FIGURE 9 is a top view of the fastener and proximal retainer of FIGURE 8;
FIGURE 10 is a cross-sectional view taken along the lines 10-10 of FIGURE 9;
FIGURE 11 is a plan view and partial cross section of the side of a link in accordance with a further alternative embodiment of the nvention;
FIGURE 12 is a plan and partial exploded view of the front of a lirlk similar to the link of FIGURE 11;
2 o FIGURE 13 is a partial exploded and partial cross-section view of a link in accordance with a further embodiment of the invention;
FIGURE 14 is a perspective view of the dowel of the link of FIGURE 13;
FIGURE 15 is a plan view of an alternate embodiment of the housing of the link, illustrating with dotted lines the inner walls of the cylirlders; and FIGURE 16 is a plan view of the top of the housing of FIGURE 15.
Detailed Description of the Invention As illustrated in FIGURES 1-5, a link 10 in accordance with the invention includes a pair of hollow cylinders or eyes 12. Each cylinder 12 defines a pair of connected or contiguous, tapered bores 14 opening in opposite directions along a common axis to define respective open ends 15.
The cylinders 12 are joined by a stem or a rod 16 so that the axes of the pairs of bores 14 are substantially parallel. Two bushing configurations preferably in the form of two pairs of b--~hings 18 are also included, and each pair is m~tingly received into a respective pair of bores 14. Each bushing 18 defines a cylindrical aperture or channel 20 along its axis.
The link 10 also includes two shafts 22, each of which is received into the respective pair of bores 14 defined by the cylinder 12 and the channels 20 defined by the respective pair of bll~hings 18. Means for retaining the shafts 22 within the bores 14 and channels 20 are also included.
The cylinders 12 and stem 16 together define a housing 24 that may be a one-piece housing made from a molded polymer or metal (see, e.g., F~GURE 1). Alternatively, the housing 24 may be a three-piece steel weldment wherein the cylinders 12 are welded to the stem 16 (see, e.g., FIGURES 2-4). In this alternative construction, the cylinders 12 may, for example, be a Monroe Shock Stock No. 11963. The stem 16 preferably has a circular cross section substantially along its length.
Each cylinder includes an inner wall 26 that defines one of the pairs of bores 14 and a central ridge 27 that divides the bores 14. The ridge 27 may define a flat face that extends parallel to the axis of the bores, or mayhave a rounded face. The inner walls 26 of each cylinder 12 adjacent each end 29 of the cylinder may be rounded (FIGURE 5).
Preferably, each shaft 22 defines a proximal end 28 and a distal end 30, both of which are threaded and include cotter pin holes 32. The distal ends 30 of shafts 22 are secured to another component of the steering 3 0 and suspension assembly. For example, the distal end 30 of one shaft 22 may be secured to the axle plate (or associated part) and the distal end of the other shaft may be secured to the stabilizer bar. The cotter pin hole 32 on the distal end 30 of the threaded shaft 22 may be used to secure a fastening nut that is used to attach the shaft to the assembly component. The diameter of the distal end 30 may be greater than the diameter of the proximal end 28.
In the embodiments of FIGURES 1-5, the means for retaining each shaft 22 within the bores 14 includes one of the pairs of bllshings 18, a pair of retainers that may be in the form of retaining washers, namely a 0 proximal washer 34 and a distal washer 35, and a fastener such as nut 36 secured to the threaded proximal end of the shaft.
Each shaft 22 includes a bushing portion 38 adjacent the proximal end 28, a tapered portion 40 adjacent the distal end 30, and a central portion 41 joining the bushing portion and the tapered portion. One 5 of the pairs of bllchings 18 and one of the distal washers 35 is disposed about the bushing portion 38 of each shaft. The diameter of the bushing portion corresponds to the diameters of the channels 20 of the b~lshings 18 and the distal washer 35, and is less than the diameters of the tapered and central portions 40, 41.
The tapered portion 40 of the shaft 22 defines a gradual inward tapering in the direction of the distal end 30 of the shaft 22 for engaging mating surfaces on the components of the steering and suspension assembly.
The central portion 41 defines a first lateral face 43 adjacent the distal end 30 and a second lateral face 45 adjacent the bushing portion 38. The bushing 25 portion defines a third lateral face 47 adjacent the proximal end 28. The shaft 22 may be constructed of any suitable metal such as a steel with an elevated hardness commonly known as "Stressproof", or of any other suitable material.
Each shaft 22 may also include a pair of diametrically-opposed 30 wrench flats 42 to be used to tighten the nuts 36. In the illustrated _ g embodiments, the wrench flats are formed on the central portion 41, extending onto the tapered portion 40. Alternatively, alternate "drive"
methods could be used, such as, for example, a hex socket broached or forged into the end of the stud. In addition, a radius corner portion 44 may be formed at the distal end of the bushing portion 41 adjacent the lateral face 45 for reducing the stress that tends to cause the formation of fractures.
Tapered or broken corner portions 60, 62 and 64 may be defined on the periphery of respective lateral faces 43, 45 and 47 to elimin~te sharp edges.
The bl-shing~ 18 desirably are substantially the same in 0 configuration and material. In the preferred embodiment, the bll~hing~ 18 are constructed of polyurethane, which has a longer life expectancy than rubber or synthetic rubber and has better shock absorbing dynamics. Polyurethane also has a relatively high degree of elasticity. Preferably, the polyurethane has a hardness of about 85 to about 95, and optimally about 90 durometers on the Shore A scale. The bushings 18 may, for example, be polyurethane bllshings that are available from Gabriel as part No. #415025, or a standard polyurethane bll~hing~ that can be obtained from Euclid.
Each bushing 18 includes a pair of flat ends 51, 53 that extend substantially perpendicular to the axes of the bores, and first and second 2 o frustoconical outer bushing walls 50, 52 that are joined together by a neck 54.
The flat ends 53 of each pair of bushings 18 are in abutting engagement within a respective cylinder 12. The outer diameters of the flat ends 51, 53 are substantially the same.
The first outer bushing wall 50 is received substantially within its respective bore 14, and the second outer bushing wall 52 extends at least partially beyond its respective bore 14. Desirably, the first outer bushing wall50 extends most of the length of the bushing 18, is tapered inwardly towards the proximal end of the bushing, and has a more gradual taper than the second outer bushing wall 52. The neck 54 may be inwardly tapered toward the first outer bushing wall, and its length is substantially less than the second outer bushing wall 52. The first outer bushing walls 50 complement the tapered bores 14. This construction elimin~tes or reduces lateral displacement of the housing 24 relative to the bllshingc 18. It also elimin~tes or reduces the longitudinal movement of each bushing 18 in the proximal direction.
Despite the advantages of the polyurethane bushing, it is appreciated that the bushings 18 can instead be constructed of any other suitable material, such as rubber or synthetic rubber. Preferably, the material chosen has a relatively long life expectancy. In this regard, some important 0 characteristics to consider in choosing a suitable material are its ability to withstand adverse weather condition and its ability to resist water, oil and ozone.
It is noted that natural and most synthetic rubbers have their best mechanical characteristics (tensile strength, elongation, compression set, etc.) when produced at a 70 durometer. Typically, the rubber is then compressed to get the hardness needed to withstand the shock loads.
Polyurethane b~lchingc, on the other hand, generally do not need the same degree of compression because of the increased hardness of polyurethane.
In the embodiments of FIGURES 1-5, each pair of proximal 2 0 and distal retaining washers 34, 35 is disposed about one of the shafts 22.
Each washer 34, 35 has an outer diameter substantially the same as or slightly less than the outer diameter of the cylinders 12. Each distal washer 35 is disposed about one of the respective bushing portions 38, and is disposed between and in abutting engagement with the flat end 53 of one of the bllchingc 18 and the lateral face 45 of one of the shafts 22. The inner diameter of the distal washers 35 complements the diameter of the bushing portion 38 and radius corner portion 44.
The proximal washer 34 is disposed about the proximal end 28 of one of the respective shafts 22, and is disposed between and in abutting 3 0 engagement with another bushing 18 and one of the nuts 36. The inner diameter of the proximal washer 34 complements the diameter of the radius corner portion 44 of the shaft ~. The inner diameter of the proximal washer 34 is less than the inner diameter of the distal washer 34.
Desirably, each washer 34, 35 includes a flat portion SS and a 5 circumferential flange 56 angled with respect to the flat portion to form a dish shape, and the flanges extend in opposite directions away from the respective pair of bll~hings 18. The flanges preferably extend at an angle of about 15 degrees to about 45 degrees and optimally at about 30 degrees. The outer diameter of the flat portion SS is about the same as the outer diameters of the flat ends 51, 53 of the bll~hing~ 18. The thicknesses of the proximal and distal washers 34, 35 may be substantially the same.
Preferably, prior to assembly, the length of the bushing portion 38 of the shaft n is less than the dimension defined by the length of one of the pairs of bllshin~s 18 plus the thickness of the flat portion SS of the distal washer 35. During assembly, however, the bllshing~ are compressed so that, in the assembled link, the length of the bushing portion 38 of the shaft 22 is about the same as the dimension defined by the length of one of the pairs of bllshings 18 plus the thickness of the flat portion SS of the distal washers 35.The flanges 56, the inward tapering of the second outer bushing walls 52 of the bushings 18, and the rounded off inner walls 26 of the cylinders 12 tend to relieve pressure on the b~l~hings when they are under compression, which can occur when the shaft n is deflected off center from absorbing road shocks. This construction provides an area in which the bushing can expand while under pressure. It also reduces the likelihood of any "pinching" of the b~lshing~ 18 between the washers and cylinders 12. The dish-shaped retaining washers 34, 35 also provides a surface for the bushing to "roll" against.
The nuts 36 may be conventional nuts but, preferably are conventional castle nuts adapted to receive a cotter pin 58 used to secure the 3 0 nuts (see FIGURE 2). The cotter pin 58 also extends through one of the cotter pin holes 32 formed on the shafts 22. Generally, application of about 55 to about 70 foot-pounds of torque will sufficiently secure the nuts to the assembly. An advantage of this construction is that it is more reliable against shock and vibration than other alternate means of securing the nut 36 to the shaft ~. Also, this construction avoids cl~ ging the threads of the shafts 22.
Alternatively, however, a nylon insert or an all metal lock nut can be used.
Examples of dimensions and materials useful for m~king the present invention are disclosed in detail in provisional U.S. patent applicationSerial No. 60/000,477 filed June 23, 1995. That entire disclosure is 0 incorporated by reference. Those of ordinary skill in the art will recognizethat various dimensions and materials can be used depending on the exact use of the present invention.
One of the advantages of the link 10 in accordance with the present invention relates to the replaceability of the individual components, such as the buchingc 18 which tend to have shorter life than the rem~ining components of the stabilizer bar. When the bllchingc 18 are no longer useful due to wear and tear (or any other reason), they can be replaced quickly and easily. Because the rest of the components can still be used, this results in cost savings each time the buchingc are replaced.
2 o If desired, all the components may be sold together (e.g., the housing 24, shafts 22, bllshingc 18, retaining washers 34, 35, nuts 36 and pins 58) in a container such as a box or bag as a kit, if desired. The components can then be assembled and installed on a vehicle. Thereafter, when the bllchingc 18 become worn, new bushingc can be obtained separately from the kit, and then can be replaced in accordance with the above. It is appreciated that other components may be individually replaced.
Additionally, some of the components which may need to be replaced on a more frequent basis may be sold together in a container such as a box or bag as a kit, if desired. When the corresponding components on the 3 o link 10 become worn, the kit can be used to replace the worn components.
For example, two pairs of bll~hings 18 and two pairs of proximal and distal retaining washers 34, 35 may be sold together as a kit for replacement of the corresponding components on the link 10. Such a kit enables the quick and easy replacement of the corresponding components.
5 The bllchings, for example, have the same configuration and are constructed of the same materials, and, thus, they can be installed quickly and easily sincevirtually no time is spent determining where each individual bushing goes.
Since the proximal and distal washers 34, 35 have different inner diameters which correspond to the portions of the shaft on which they are to be 0 installed, they also can be installed relatively quickly.
If desired, the kit may also include one pair of nuts 36 to avoid having to reuse nuts that may be difficult to re-install due to corrosion or wear and tear. If the nuts are castle nuts, a pair of cotter pins may also be included as part of the kit to enhance the quick and easy replacement of the 5 castle nuts.
FIGURES 6-10 illustrate an alternative embodiment of the link 210 wherein the proximal retainer is unitary, and preferably integral, with its corresponding fastener; and the distal retainer is unitary, and preferably integral, with its corresponding shaft. As used herein, the term "integral" is 20 intended to refer to a single structure that has a one-piece or monolithic-type construction; and the term "unitary" is intended to refer to a structure comprised of components that are fixedly connected or mounted together in any suitable manner, including being integral.
The embodiment of FIGURES 6-10 further facilitates quick 25 and easy assembly of the link and the ready replacement of various components because each proximal retainer and corresponding fastener are not separately assembled on the shaft and because the distal retainers do not have to be assembled on the shafts.
With this embodiment, a pair of fasteners 270, engageable with the proximal ends 228 of the shafts 222, are defined. The proximal retainer preferably is in the form of a lip or ring 271 having first and second sides 272and 273. Each ring 271 is unitary with the respective fastener 270. The first side 272 of each ring 271 defines a generally circular and generally flat portion or face 274 facing or abutting the flat end 253 of one of the bushings 218. The outer diameter of the ring 271 is substantially the same as or slightly less than the outer diameter of the cylinders 212.
The circular flange 256 preferably is in the form of a beveled edge that extends around a periphery of the face 274, preferably extending away from the bushing 218 to relieve pressure on the b~l~hings when they are lO under compression. The circular flange 256 may extend at an angle of about 15 degrees to about 45 degrees, and optimally at about 30 degrees.
Each fastener 270 includes a plurality of parallel eng~ging fingers 275, preferably six, extending from the second side 273 of each ring 271. Each eng~ging finger 275 defines an inwardly-facing wall 276. The eng~ging fingers 275 on each ring 271 may be interconnected at their bases by an apron 277. In the illustrated embodiment, each engaging finger 275 has a generally pentagonal cross section, and the top of each finger includes a tapered outer portion 279.
A hole 280 for receiving the threaded proximal end 228 of one 20 of the shafts 222 is defined in each fastener 270 preferably by an inner wall282 and the inwardly-facing walls 276. Preferably, both the inner wall 282 and the inwardly-facing walls 276 are threaded for eng~ging the threaded proximal end ~s of the shaft 222. The eng~ging fingers 275 may be configured to receive one of the cotter pins 258 to secure the fasteners 270 to 25 the shafts 222. The eng~ging fingers 275 may also include a radiused corner portion 284 defined adjacent the second sides 206 of the ring 202.
The pair of distal retainers are defined by a pair of lips or rings 290, each of which is unitary with the respective shaft 222 proximal of the distal end 230 of the shaft 222. Each ring 290 defines first and second sides 291 and 292. The first side 291 of each ring 290 defines a generally circular and generally flat portion or face 293 facing or abutting the flat end 253 of one of the bll~hing~ 218. The ring 290 has an outer diameter substantially the same as or slightly less than the outer diameter of the cylinders 212.
The circular flange 256 on the ring 290 preferably is in the form of a beveled edge that extends around a periphery of the face 293, preferably extending away from the bushing 218 to relieve pressure. The circular flange may extend at an angle of about 15 degrees to about 45 degrees and optimally at about 30 degrees.
Each ring 271 and the corresponding fastener 270 are unitary, 0 and thus they may be integral as shown in the embodiment of FIGURES 6-10 or fixedly connected or mounted together in any other suitable manner.
Similarly, each ring 290 and the corresponding shaft 222 are unitary, and thus they may be integral as shown in the embodiment of FIGURES 6-10 or fixedly connected or mounted together in any other suitable manner.
Radiused corner portions 295 may be defined between the ring 290 and the bushing portion 238 and between the ring 290 and the central portion 241.
The embodiment of FIGURES 6-10 also can be sold together in a container. For example, the housing 224, the pair of shafts 222, two pairs of b~l~hing~ 218, and the pair of fasteners 270 and unitary proximal rings 271 20 may be sold in a container. Additionally, some of the components that need to be replaced on a frequent basis, such as the bllshings 218 and the fasteners 270 and unitary proximal rings 271, may be sold together in a container, such as a bag or box, as a replacement kit. The pair of cotter pins 258 may also be included as part of the kit.
FIGURES 11 and 12 illustrate still another alternative embodiment of the link 310 wherein the housing 324 is of a design commonly referred to as "gooseneck" and the cylinders 312 are joined by the goosenecked stem 316 so that the axes of the pairs of bores 314 are substantially perpendicular. The shafts 322 are similar to those described in 30 reference to the embodiment of FIGURES 6-10. This feature further facilitates quick and easy assembly of the link 310 due to the unitary, and preferably integral design.
In this embodiment, cylinder 312 defines a pair of tapered bores 314 having an axis, while cylinder 313 defines a pair of tapered bores 315 also having an axis. Unlike previous embodiments, however, the two axes are in a spaced perpendicular relationship to each other, as shown in FIGURE 12.
With respect to stem 316, there are two curves forming the gooseneck design.
Similar to the previous embodiments, the embodiment of FIGURES 11 and 12 may be sold together in a container. Frequently replaced components, such as b~lching~ 318 and fasteners 370, may be sold together in a replacement kit.
Yet another alternate embodiment of the invention is the link 410 shown in FIGURE 13.
Shaft 422 of FIGURE 13 includes a cylindrical mounting portion 439 for engaging mating surfaces of components 495 of the vehicle such as the steering and suspension assembly or a mounting bracket. Shaft 422 is similar to those described in reference to the embodiment of FIGURES 6 and 7 except that shaft 422 may not include tapered portion 240.
Instead, the cylindrical mounting portion 439 may be included on shaft 422 2 o between the bushing portion 438 and the distal end 430.
The cylindrical mounting portion 439 allows the shaft 422 to be mounted into a tapered mounting hole 496, as shown in FIGURE 13, from the opposite side of the vehicle component 495 defining the mounting hole 496. While the shaft 2~ of FIGURES 6 and 7 is inserted into the mounting hole such that the tapered portion 240 of the shaft 222 mates with the tapered mounting hole, the cylindrical mounting portion 439 of shaft 422 of FIGURE
13 can be mounted through the opposite side, i.e. through the narrower side of the tapered mounting hole 496, when a dowel 401 is inserted into the mounting hole 496. When the link 410 is mounted from the opposite side of the vehicle component 495, the link 410 may avoid interfering with other components of the vehicle suspension such as the radius rod.
The dowel 401 is inserted into the mounting hole 496 as shown in FIGURE 13. FIGURE 14 illustrates an embodiment of the dowel 401 that includes a tapered outer surface 402 and a substantially cylindrical inner surface 403. The tapered surface 402 is configured to be accepted into the mounting hold 496, and in turn, the shaft 422 can be mounted through the dowel 401. This configuration allows a cylindrical shaft to be mounted into a tapered hole. The dowel 401 fills the space between the surfaces of the shaft and the hole when the two surfaces are not m~tingly configured.
Alternatively, the inner and outer surface of the dowel 401 can have any shape or configuration necessary to be m~tingly accommodated within any mounting hole and around any shaft. For example, the shaft can have a tapered section and the mounting hole can be cylindrical. This alternate configuration would require the dowel to have a cylindrical outer surface and a tapered inner surface.
The dowel 401 may also define a substantially longitudinal slot 404 as shown in FIGURES 13 and 14. The slot 404 allows the diameter of the dowel 401 to be variable so that the dowel 401 can fit into mounting holes whose diameters may vary due to m~mlf~cturing tolerances or so that a dowel of a standard size can fit into holes within a certain range of diameters.
Referring again to FIGURE 13, a unitary distal retainer 490 preferably is provided on shaft 4~ between the mounting portion 439 and the bushing portion 438. The distal retainer has a first side 491 and a second side 492. The first side 491 defines a generally flat portion 493 facing or abutting one of the bll~hings 418. The second side 492 defines a concentric groove 494. The concentric groove 494 provides a stress relief for the shaft 422 as the shaft flexes. Additionally, a distal washer 435 may be disposed about the shaft 422 between the distal retainer 490 and the vehicle mounting component 3 0 495. In the embodiment shown in FIGURE 13, the washer 435 includes a flat portion 455 that abuts the second side 492 of the distal retainer 490 and a flange portion 456 that is angled toward the distal retainer 490. The washer 435 protects the mounting component 495 from gouging by the distal retainer 490 that can occur as the shaft vibrates or flexes in use. A distal fastener 436is used to secure the link 410 to the vehicle.
Another alternate embodiment of the invention comprises a shaft with an integral or unitary proximal retainer that abuts the bushing configuration while a distal fastener mounted to the distal end of the shaft holds the proximal retainer so that the bushing configuration is held within 0 the cylinder and against the mounting component.
The embodiments of FIGURES 13 and 14 may be sold together in a container. Frequently replaced components, such as the bllshings 418, fasteners 436 and 470, and dowel 401, may be sold together or separately in a replacement kit or kits.
FIGURES 15 and 16 show an alternate embodiment of the housing 524 that includes cylinders 512 and stem 516. The stem 516 of the embodiment shown in FIGURES 15 and 16, may define a recess 517 that can be used for a logo or emblem.
The foregoing description is for purposes of illustration only and 20 is not intended to limit the scope of protection accorded this invention. Thescope of protection is to be measured by the following claims, which should be interpreted as broadly as the inventive contribution permits.
Technical Field of the Invention The present invention relates to a stabilizer or torsion bar link that can be used to stabilize the suspension for a vehicle, such as, for 5 example, a bus or a car.
Ba~k~ound of the Invention A suspension assembly for a bus or other vehicle usually includes, among other components, a torsion bar and a connecting link. The torsion bar (which also may be called a stabilizer or sway bar) is generally 10 affixed to the vehicle frame with the link functioning as the connecting member to the axle. The torsion bar absorbs torsional loading while the link additionally must act as a shock absorber.
The link can have a generally U-shaped construction that includes a metal housing and a pair of metal shafts permanently secured to 5 the housing. The shafts are also connected to other components of the assembly, such as the axle plate (or associated part) and the torsion bar.
It is known to use rubber as an intermediary to permanently secure the shafts to the housing to add flexibility to the link so that the link is better able to absorb road shocks. To construct such a link, rubber is molded 2 o to one end of each shaft. The ends of the shaft are then inserted into the bores defined in the housing. The housing is crimped radially around each bore to permanently secure the shafts to the housing.
A disadvantage of this known link, however, is that it has a relatively short life expectancy because the rubber tends to shear or become 25 worn relatively quickly and much sooner than the rest of the components.
Thus, once the rubber shears or becomes worn, the entire link is no longer useful and must be replaced.
In an attempt to provide a more durable link, an all metal link that uses all metal ball studs has been developed. This link is undesirable 3 0 because it lacks flexibility and does not absorb road shocks as well as the other link. In addition, it has been noted as the source of suspension squeak.
As a result, the all metal link tends to transfer stress to the suspension which, over time, will shorten the life of various parts in the suspension.
What is needed is a link that is capable of effectively absorbing 5 road shocks better than the prior art links, and that is more economical than the prior art links. Such a link should include a flexible element to absorb the shocks, but should also address the problem of short life expectancy associated with the known link having a flexible element. Such a link preferably is easy to assemble. The present invention meets these desires.
10 Summaly of the Invention The present invention provides a link for a steering and suspension assembly for a bus or other vehicle. In its preferred embodiment, it includes a pair of shafts or studs, and a housing that is defined by a pair of eyes or cylinders that are joined together by a rod or stem. Each cylinder 5 defines a pair of adjoining or contiguous, tapered bores opening in opposite directions for receiving a pair of bll~hings.
Preferably, both ends of each shaft are threaded, with a distal threaded end of each shaft being secured to another component of the assembly such as the axle plate (or associated part) or torsion bar. Each shaft 20 may be readily secured to the housing by replaceable components, such as, a pair of proximal and distal retainers, a pair of bll~hings, and a fastener such as a nut secured to a proximal threaded end of the shaft. In one preferred embodiment, the proximal and distal retainers are in the form of proximal and distal retaining washers. In an alternative preferred embodiment, each 25 proximal retainer is in the form of a proximal ring that is integral or unitary with its corresponding fastener, and each distal retainer is in the form of a distal ring that is integral or unitary with its corresponding shaft.
In another alternate embodiment, the link comprises a hollow cylinder including a pair of open ends; a stem associated with the cylinder for 30 mounting the cylinder to the vehicle; a bushing configuration, a shaft, and fastening elements similar to those of the preferred embodiment; and a hollow cylindrical dowel. The dowel is associated with the shaft, and is configured to be accepted into a mounting hole on a component of the steering or suspension assembly.
The dowel of this alternate embodiment allows the link to be installed on the vehicle from the opposite side of the component to avoid possible interference with another component of the suspension or steering assemblies such as a radius rod. Also, the dowel can be configured to adapt a cylindrical shaft to a tapered mounting hole or vice-versa. The dowel may, in lo fact, have a number of configurations so that a shaft having one shape can fit into mounting holes of any shape.
The bllshings preferably are constructed of polyurethane, which has a longer life expectancy than rubber or synthetic rubber and has better shock absorbing dynamics. Polyurethane also has a relatively high degree of elasticity. Preferably, the polyurethane has a hardness of about 85 to about 95 durometers on the Shore A scale, and optimally about 90 durometers.
Alternatively, the bllching~ may be constructed of rubber or synthetic rubber that preferably has a hardness of about 70 durometers.
Each pair of bushings is received within one of the respective 20 pairs of bores defined by the cylinders. Desirably, each bushing has a first frustoconical wall with a taper that narrows toward the end of the bushing.
The ffrst frustoconical outer walls preferably complement the tapered bores.
This construction elimin~tes or reduces lateral displacement of the housing relative to the bll~hing~ and shaft. The tapers also elimin~te or reduce 25 longitudinal displacement of each bushing in the direction of its adjacent bushing.
Each bushing may also have a second frustoconical outer wall with a taper that narrows toward the other end of the bushing, which extends outside the bore. This construction tends to relieve pressure and avoid pinching of the bushing between the washers and the cylinders when the bushing is under compression during service.
Preferably, the retainers are disposed about the shafts, and abut the ends of the bnshingc that extend outside the bores. If retaining washers 5 are employed, the holes defined by the proximal and distal retaining washers preferably are different sizes.
Each retainer may have a circumferential flange angled with respect to a flat portion. The flanges of each pair of proximal and distal retainers face away from the bnshing~, which also helps to relieve pressure 0 when the bushing is under compression yet still contain the bnshings in the housings. With this construction, when the shaft is deflected from center, it causes further compression of the bn~hing.c The orientation of the retainers allows relief from this compression. The flanges also provide a surface for the bushing to "roll" against.
The fasteners may be conventional castle nuts or may otherwise be adapted to engage a cotter pin for securing the fasteners. With this embodiment, one of the threaded ends of the shaft also defines a cotter pin hole for receiving the cotter pin. This construction tends to be more reliable against shock and vibration than other alternatives, and also avoids call~ing 20 damage to the threads of the shafts. Alternatively, however, a nylon insert nut or an all metal lock nut can be used.
The preferred embodiment of the present invention provides a link that is more economical than the prior art links because its components can be easily and quickly replaced when they fail or become worn. As a 25 result, the link can be reused and does not have to be discarded when one of its components fails or becomes worn.
In this regard, cost savings likely will be appreciated most in connection with the replacement of bll~hings since they tend to have substantially shorter lives than the rest of the components of the link and also3 0 tend to be significantly less expensive than the housing and shafts. Thus, with the present invention, the bllshing~ can be continuously replaced as they become worn, thereby substantially extending the life of the link.
If desired, the link may be sold together as a fully-assembled link. Alternatively, all of the components may be sold together (e.g. the housing, retainers, bllshing~, fasteners and pins) in a container such as a box or bag as a kit, if desired. The components can then be assembled and installed on a vehicle. Thereafter, when the bllshings (or other components) become worn, new bllshings (or other components) can be obtained separately from the kit, and then can be replaced.
0 Similarly, the components that tend to be replaced more frequently can also be sold together as a kit. For example, two pairs of bllshing~, two pairs of retainers, a pair of fasteners and a pair of cotter pinsmay be sold together in a package to be used when any or all of these original (or previously replaced) components become worn. In an alternative embodiment described above, the kit may include two pairs of bll~hing~, the pair of fasteners each with unitary proximal retainers, and a pair of cotter pins. Such a kit enables quick and easy replacement of the corresponding components.
Numerous other advantages and features of the present 2 o invention will become readily apparent from the following detailed description of the invention and the embodiments thereof, from the claims and from the accompanying drawings.
Brief Description of the Drawin~c FIGURE 1 is an exploded perspective view of a link in accordance with one embodiment of the invention;
FIGURE 2 is a partial exploded and partial cross section view of a link similar to the link of FIGURE 1;
FIGURE 3 is a plan view of the side of the housing of the link of FIGURE 2, illustrating with dotted lines the inner walls of the cylinders;
FIGURE 4 is a plan view of the top of the housing of FIGURE 3;
FIGURE S is a cross section view taken along the lines S-S of FIGURE 4;
FIGURE 6 is a broken and partial cross section view of a link in accordance with a further alternative embodiment of the invention;
FIGURE 7 is a side elevational view of the shaft of the link of FIGURE 6;
FIGURE 8 is a side elevational view of an integral fastener and proximal retainer of the link of FIGURE 6;
FIGURE 9 is a top view of the fastener and proximal retainer of FIGURE 8;
FIGURE 10 is a cross-sectional view taken along the lines 10-10 of FIGURE 9;
FIGURE 11 is a plan view and partial cross section of the side of a link in accordance with a further alternative embodiment of the nvention;
FIGURE 12 is a plan and partial exploded view of the front of a lirlk similar to the link of FIGURE 11;
2 o FIGURE 13 is a partial exploded and partial cross-section view of a link in accordance with a further embodiment of the invention;
FIGURE 14 is a perspective view of the dowel of the link of FIGURE 13;
FIGURE 15 is a plan view of an alternate embodiment of the housing of the link, illustrating with dotted lines the inner walls of the cylirlders; and FIGURE 16 is a plan view of the top of the housing of FIGURE 15.
Detailed Description of the Invention As illustrated in FIGURES 1-5, a link 10 in accordance with the invention includes a pair of hollow cylinders or eyes 12. Each cylinder 12 defines a pair of connected or contiguous, tapered bores 14 opening in opposite directions along a common axis to define respective open ends 15.
The cylinders 12 are joined by a stem or a rod 16 so that the axes of the pairs of bores 14 are substantially parallel. Two bushing configurations preferably in the form of two pairs of b--~hings 18 are also included, and each pair is m~tingly received into a respective pair of bores 14. Each bushing 18 defines a cylindrical aperture or channel 20 along its axis.
The link 10 also includes two shafts 22, each of which is received into the respective pair of bores 14 defined by the cylinder 12 and the channels 20 defined by the respective pair of bll~hings 18. Means for retaining the shafts 22 within the bores 14 and channels 20 are also included.
The cylinders 12 and stem 16 together define a housing 24 that may be a one-piece housing made from a molded polymer or metal (see, e.g., F~GURE 1). Alternatively, the housing 24 may be a three-piece steel weldment wherein the cylinders 12 are welded to the stem 16 (see, e.g., FIGURES 2-4). In this alternative construction, the cylinders 12 may, for example, be a Monroe Shock Stock No. 11963. The stem 16 preferably has a circular cross section substantially along its length.
Each cylinder includes an inner wall 26 that defines one of the pairs of bores 14 and a central ridge 27 that divides the bores 14. The ridge 27 may define a flat face that extends parallel to the axis of the bores, or mayhave a rounded face. The inner walls 26 of each cylinder 12 adjacent each end 29 of the cylinder may be rounded (FIGURE 5).
Preferably, each shaft 22 defines a proximal end 28 and a distal end 30, both of which are threaded and include cotter pin holes 32. The distal ends 30 of shafts 22 are secured to another component of the steering 3 0 and suspension assembly. For example, the distal end 30 of one shaft 22 may be secured to the axle plate (or associated part) and the distal end of the other shaft may be secured to the stabilizer bar. The cotter pin hole 32 on the distal end 30 of the threaded shaft 22 may be used to secure a fastening nut that is used to attach the shaft to the assembly component. The diameter of the distal end 30 may be greater than the diameter of the proximal end 28.
In the embodiments of FIGURES 1-5, the means for retaining each shaft 22 within the bores 14 includes one of the pairs of bllshings 18, a pair of retainers that may be in the form of retaining washers, namely a 0 proximal washer 34 and a distal washer 35, and a fastener such as nut 36 secured to the threaded proximal end of the shaft.
Each shaft 22 includes a bushing portion 38 adjacent the proximal end 28, a tapered portion 40 adjacent the distal end 30, and a central portion 41 joining the bushing portion and the tapered portion. One 5 of the pairs of bllchings 18 and one of the distal washers 35 is disposed about the bushing portion 38 of each shaft. The diameter of the bushing portion corresponds to the diameters of the channels 20 of the b~lshings 18 and the distal washer 35, and is less than the diameters of the tapered and central portions 40, 41.
The tapered portion 40 of the shaft 22 defines a gradual inward tapering in the direction of the distal end 30 of the shaft 22 for engaging mating surfaces on the components of the steering and suspension assembly.
The central portion 41 defines a first lateral face 43 adjacent the distal end 30 and a second lateral face 45 adjacent the bushing portion 38. The bushing 25 portion defines a third lateral face 47 adjacent the proximal end 28. The shaft 22 may be constructed of any suitable metal such as a steel with an elevated hardness commonly known as "Stressproof", or of any other suitable material.
Each shaft 22 may also include a pair of diametrically-opposed 30 wrench flats 42 to be used to tighten the nuts 36. In the illustrated _ g embodiments, the wrench flats are formed on the central portion 41, extending onto the tapered portion 40. Alternatively, alternate "drive"
methods could be used, such as, for example, a hex socket broached or forged into the end of the stud. In addition, a radius corner portion 44 may be formed at the distal end of the bushing portion 41 adjacent the lateral face 45 for reducing the stress that tends to cause the formation of fractures.
Tapered or broken corner portions 60, 62 and 64 may be defined on the periphery of respective lateral faces 43, 45 and 47 to elimin~te sharp edges.
The bl-shing~ 18 desirably are substantially the same in 0 configuration and material. In the preferred embodiment, the bll~hing~ 18 are constructed of polyurethane, which has a longer life expectancy than rubber or synthetic rubber and has better shock absorbing dynamics. Polyurethane also has a relatively high degree of elasticity. Preferably, the polyurethane has a hardness of about 85 to about 95, and optimally about 90 durometers on the Shore A scale. The bushings 18 may, for example, be polyurethane bllshings that are available from Gabriel as part No. #415025, or a standard polyurethane bll~hing~ that can be obtained from Euclid.
Each bushing 18 includes a pair of flat ends 51, 53 that extend substantially perpendicular to the axes of the bores, and first and second 2 o frustoconical outer bushing walls 50, 52 that are joined together by a neck 54.
The flat ends 53 of each pair of bushings 18 are in abutting engagement within a respective cylinder 12. The outer diameters of the flat ends 51, 53 are substantially the same.
The first outer bushing wall 50 is received substantially within its respective bore 14, and the second outer bushing wall 52 extends at least partially beyond its respective bore 14. Desirably, the first outer bushing wall50 extends most of the length of the bushing 18, is tapered inwardly towards the proximal end of the bushing, and has a more gradual taper than the second outer bushing wall 52. The neck 54 may be inwardly tapered toward the first outer bushing wall, and its length is substantially less than the second outer bushing wall 52. The first outer bushing walls 50 complement the tapered bores 14. This construction elimin~tes or reduces lateral displacement of the housing 24 relative to the bllshingc 18. It also elimin~tes or reduces the longitudinal movement of each bushing 18 in the proximal direction.
Despite the advantages of the polyurethane bushing, it is appreciated that the bushings 18 can instead be constructed of any other suitable material, such as rubber or synthetic rubber. Preferably, the material chosen has a relatively long life expectancy. In this regard, some important 0 characteristics to consider in choosing a suitable material are its ability to withstand adverse weather condition and its ability to resist water, oil and ozone.
It is noted that natural and most synthetic rubbers have their best mechanical characteristics (tensile strength, elongation, compression set, etc.) when produced at a 70 durometer. Typically, the rubber is then compressed to get the hardness needed to withstand the shock loads.
Polyurethane b~lchingc, on the other hand, generally do not need the same degree of compression because of the increased hardness of polyurethane.
In the embodiments of FIGURES 1-5, each pair of proximal 2 0 and distal retaining washers 34, 35 is disposed about one of the shafts 22.
Each washer 34, 35 has an outer diameter substantially the same as or slightly less than the outer diameter of the cylinders 12. Each distal washer 35 is disposed about one of the respective bushing portions 38, and is disposed between and in abutting engagement with the flat end 53 of one of the bllchingc 18 and the lateral face 45 of one of the shafts 22. The inner diameter of the distal washers 35 complements the diameter of the bushing portion 38 and radius corner portion 44.
The proximal washer 34 is disposed about the proximal end 28 of one of the respective shafts 22, and is disposed between and in abutting 3 0 engagement with another bushing 18 and one of the nuts 36. The inner diameter of the proximal washer 34 complements the diameter of the radius corner portion 44 of the shaft ~. The inner diameter of the proximal washer 34 is less than the inner diameter of the distal washer 34.
Desirably, each washer 34, 35 includes a flat portion SS and a 5 circumferential flange 56 angled with respect to the flat portion to form a dish shape, and the flanges extend in opposite directions away from the respective pair of bll~hings 18. The flanges preferably extend at an angle of about 15 degrees to about 45 degrees and optimally at about 30 degrees. The outer diameter of the flat portion SS is about the same as the outer diameters of the flat ends 51, 53 of the bll~hing~ 18. The thicknesses of the proximal and distal washers 34, 35 may be substantially the same.
Preferably, prior to assembly, the length of the bushing portion 38 of the shaft n is less than the dimension defined by the length of one of the pairs of bllshin~s 18 plus the thickness of the flat portion SS of the distal washer 35. During assembly, however, the bllshing~ are compressed so that, in the assembled link, the length of the bushing portion 38 of the shaft 22 is about the same as the dimension defined by the length of one of the pairs of bllshings 18 plus the thickness of the flat portion SS of the distal washers 35.The flanges 56, the inward tapering of the second outer bushing walls 52 of the bushings 18, and the rounded off inner walls 26 of the cylinders 12 tend to relieve pressure on the b~l~hings when they are under compression, which can occur when the shaft n is deflected off center from absorbing road shocks. This construction provides an area in which the bushing can expand while under pressure. It also reduces the likelihood of any "pinching" of the b~lshing~ 18 between the washers and cylinders 12. The dish-shaped retaining washers 34, 35 also provides a surface for the bushing to "roll" against.
The nuts 36 may be conventional nuts but, preferably are conventional castle nuts adapted to receive a cotter pin 58 used to secure the 3 0 nuts (see FIGURE 2). The cotter pin 58 also extends through one of the cotter pin holes 32 formed on the shafts 22. Generally, application of about 55 to about 70 foot-pounds of torque will sufficiently secure the nuts to the assembly. An advantage of this construction is that it is more reliable against shock and vibration than other alternate means of securing the nut 36 to the shaft ~. Also, this construction avoids cl~ ging the threads of the shafts 22.
Alternatively, however, a nylon insert or an all metal lock nut can be used.
Examples of dimensions and materials useful for m~king the present invention are disclosed in detail in provisional U.S. patent applicationSerial No. 60/000,477 filed June 23, 1995. That entire disclosure is 0 incorporated by reference. Those of ordinary skill in the art will recognizethat various dimensions and materials can be used depending on the exact use of the present invention.
One of the advantages of the link 10 in accordance with the present invention relates to the replaceability of the individual components, such as the buchingc 18 which tend to have shorter life than the rem~ining components of the stabilizer bar. When the bllchingc 18 are no longer useful due to wear and tear (or any other reason), they can be replaced quickly and easily. Because the rest of the components can still be used, this results in cost savings each time the buchingc are replaced.
2 o If desired, all the components may be sold together (e.g., the housing 24, shafts 22, bllshingc 18, retaining washers 34, 35, nuts 36 and pins 58) in a container such as a box or bag as a kit, if desired. The components can then be assembled and installed on a vehicle. Thereafter, when the bllchingc 18 become worn, new bushingc can be obtained separately from the kit, and then can be replaced in accordance with the above. It is appreciated that other components may be individually replaced.
Additionally, some of the components which may need to be replaced on a more frequent basis may be sold together in a container such as a box or bag as a kit, if desired. When the corresponding components on the 3 o link 10 become worn, the kit can be used to replace the worn components.
For example, two pairs of bll~hings 18 and two pairs of proximal and distal retaining washers 34, 35 may be sold together as a kit for replacement of the corresponding components on the link 10. Such a kit enables the quick and easy replacement of the corresponding components.
5 The bllchings, for example, have the same configuration and are constructed of the same materials, and, thus, they can be installed quickly and easily sincevirtually no time is spent determining where each individual bushing goes.
Since the proximal and distal washers 34, 35 have different inner diameters which correspond to the portions of the shaft on which they are to be 0 installed, they also can be installed relatively quickly.
If desired, the kit may also include one pair of nuts 36 to avoid having to reuse nuts that may be difficult to re-install due to corrosion or wear and tear. If the nuts are castle nuts, a pair of cotter pins may also be included as part of the kit to enhance the quick and easy replacement of the 5 castle nuts.
FIGURES 6-10 illustrate an alternative embodiment of the link 210 wherein the proximal retainer is unitary, and preferably integral, with its corresponding fastener; and the distal retainer is unitary, and preferably integral, with its corresponding shaft. As used herein, the term "integral" is 20 intended to refer to a single structure that has a one-piece or monolithic-type construction; and the term "unitary" is intended to refer to a structure comprised of components that are fixedly connected or mounted together in any suitable manner, including being integral.
The embodiment of FIGURES 6-10 further facilitates quick 25 and easy assembly of the link and the ready replacement of various components because each proximal retainer and corresponding fastener are not separately assembled on the shaft and because the distal retainers do not have to be assembled on the shafts.
With this embodiment, a pair of fasteners 270, engageable with the proximal ends 228 of the shafts 222, are defined. The proximal retainer preferably is in the form of a lip or ring 271 having first and second sides 272and 273. Each ring 271 is unitary with the respective fastener 270. The first side 272 of each ring 271 defines a generally circular and generally flat portion or face 274 facing or abutting the flat end 253 of one of the bushings 218. The outer diameter of the ring 271 is substantially the same as or slightly less than the outer diameter of the cylinders 212.
The circular flange 256 preferably is in the form of a beveled edge that extends around a periphery of the face 274, preferably extending away from the bushing 218 to relieve pressure on the b~l~hings when they are lO under compression. The circular flange 256 may extend at an angle of about 15 degrees to about 45 degrees, and optimally at about 30 degrees.
Each fastener 270 includes a plurality of parallel eng~ging fingers 275, preferably six, extending from the second side 273 of each ring 271. Each eng~ging finger 275 defines an inwardly-facing wall 276. The eng~ging fingers 275 on each ring 271 may be interconnected at their bases by an apron 277. In the illustrated embodiment, each engaging finger 275 has a generally pentagonal cross section, and the top of each finger includes a tapered outer portion 279.
A hole 280 for receiving the threaded proximal end 228 of one 20 of the shafts 222 is defined in each fastener 270 preferably by an inner wall282 and the inwardly-facing walls 276. Preferably, both the inner wall 282 and the inwardly-facing walls 276 are threaded for eng~ging the threaded proximal end ~s of the shaft 222. The eng~ging fingers 275 may be configured to receive one of the cotter pins 258 to secure the fasteners 270 to 25 the shafts 222. The eng~ging fingers 275 may also include a radiused corner portion 284 defined adjacent the second sides 206 of the ring 202.
The pair of distal retainers are defined by a pair of lips or rings 290, each of which is unitary with the respective shaft 222 proximal of the distal end 230 of the shaft 222. Each ring 290 defines first and second sides 291 and 292. The first side 291 of each ring 290 defines a generally circular and generally flat portion or face 293 facing or abutting the flat end 253 of one of the bll~hing~ 218. The ring 290 has an outer diameter substantially the same as or slightly less than the outer diameter of the cylinders 212.
The circular flange 256 on the ring 290 preferably is in the form of a beveled edge that extends around a periphery of the face 293, preferably extending away from the bushing 218 to relieve pressure. The circular flange may extend at an angle of about 15 degrees to about 45 degrees and optimally at about 30 degrees.
Each ring 271 and the corresponding fastener 270 are unitary, 0 and thus they may be integral as shown in the embodiment of FIGURES 6-10 or fixedly connected or mounted together in any other suitable manner.
Similarly, each ring 290 and the corresponding shaft 222 are unitary, and thus they may be integral as shown in the embodiment of FIGURES 6-10 or fixedly connected or mounted together in any other suitable manner.
Radiused corner portions 295 may be defined between the ring 290 and the bushing portion 238 and between the ring 290 and the central portion 241.
The embodiment of FIGURES 6-10 also can be sold together in a container. For example, the housing 224, the pair of shafts 222, two pairs of b~l~hing~ 218, and the pair of fasteners 270 and unitary proximal rings 271 20 may be sold in a container. Additionally, some of the components that need to be replaced on a frequent basis, such as the bllshings 218 and the fasteners 270 and unitary proximal rings 271, may be sold together in a container, such as a bag or box, as a replacement kit. The pair of cotter pins 258 may also be included as part of the kit.
FIGURES 11 and 12 illustrate still another alternative embodiment of the link 310 wherein the housing 324 is of a design commonly referred to as "gooseneck" and the cylinders 312 are joined by the goosenecked stem 316 so that the axes of the pairs of bores 314 are substantially perpendicular. The shafts 322 are similar to those described in 30 reference to the embodiment of FIGURES 6-10. This feature further facilitates quick and easy assembly of the link 310 due to the unitary, and preferably integral design.
In this embodiment, cylinder 312 defines a pair of tapered bores 314 having an axis, while cylinder 313 defines a pair of tapered bores 315 also having an axis. Unlike previous embodiments, however, the two axes are in a spaced perpendicular relationship to each other, as shown in FIGURE 12.
With respect to stem 316, there are two curves forming the gooseneck design.
Similar to the previous embodiments, the embodiment of FIGURES 11 and 12 may be sold together in a container. Frequently replaced components, such as b~lching~ 318 and fasteners 370, may be sold together in a replacement kit.
Yet another alternate embodiment of the invention is the link 410 shown in FIGURE 13.
Shaft 422 of FIGURE 13 includes a cylindrical mounting portion 439 for engaging mating surfaces of components 495 of the vehicle such as the steering and suspension assembly or a mounting bracket. Shaft 422 is similar to those described in reference to the embodiment of FIGURES 6 and 7 except that shaft 422 may not include tapered portion 240.
Instead, the cylindrical mounting portion 439 may be included on shaft 422 2 o between the bushing portion 438 and the distal end 430.
The cylindrical mounting portion 439 allows the shaft 422 to be mounted into a tapered mounting hole 496, as shown in FIGURE 13, from the opposite side of the vehicle component 495 defining the mounting hole 496. While the shaft 2~ of FIGURES 6 and 7 is inserted into the mounting hole such that the tapered portion 240 of the shaft 222 mates with the tapered mounting hole, the cylindrical mounting portion 439 of shaft 422 of FIGURE
13 can be mounted through the opposite side, i.e. through the narrower side of the tapered mounting hole 496, when a dowel 401 is inserted into the mounting hole 496. When the link 410 is mounted from the opposite side of the vehicle component 495, the link 410 may avoid interfering with other components of the vehicle suspension such as the radius rod.
The dowel 401 is inserted into the mounting hole 496 as shown in FIGURE 13. FIGURE 14 illustrates an embodiment of the dowel 401 that includes a tapered outer surface 402 and a substantially cylindrical inner surface 403. The tapered surface 402 is configured to be accepted into the mounting hold 496, and in turn, the shaft 422 can be mounted through the dowel 401. This configuration allows a cylindrical shaft to be mounted into a tapered hole. The dowel 401 fills the space between the surfaces of the shaft and the hole when the two surfaces are not m~tingly configured.
Alternatively, the inner and outer surface of the dowel 401 can have any shape or configuration necessary to be m~tingly accommodated within any mounting hole and around any shaft. For example, the shaft can have a tapered section and the mounting hole can be cylindrical. This alternate configuration would require the dowel to have a cylindrical outer surface and a tapered inner surface.
The dowel 401 may also define a substantially longitudinal slot 404 as shown in FIGURES 13 and 14. The slot 404 allows the diameter of the dowel 401 to be variable so that the dowel 401 can fit into mounting holes whose diameters may vary due to m~mlf~cturing tolerances or so that a dowel of a standard size can fit into holes within a certain range of diameters.
Referring again to FIGURE 13, a unitary distal retainer 490 preferably is provided on shaft 4~ between the mounting portion 439 and the bushing portion 438. The distal retainer has a first side 491 and a second side 492. The first side 491 defines a generally flat portion 493 facing or abutting one of the bll~hings 418. The second side 492 defines a concentric groove 494. The concentric groove 494 provides a stress relief for the shaft 422 as the shaft flexes. Additionally, a distal washer 435 may be disposed about the shaft 422 between the distal retainer 490 and the vehicle mounting component 3 0 495. In the embodiment shown in FIGURE 13, the washer 435 includes a flat portion 455 that abuts the second side 492 of the distal retainer 490 and a flange portion 456 that is angled toward the distal retainer 490. The washer 435 protects the mounting component 495 from gouging by the distal retainer 490 that can occur as the shaft vibrates or flexes in use. A distal fastener 436is used to secure the link 410 to the vehicle.
Another alternate embodiment of the invention comprises a shaft with an integral or unitary proximal retainer that abuts the bushing configuration while a distal fastener mounted to the distal end of the shaft holds the proximal retainer so that the bushing configuration is held within 0 the cylinder and against the mounting component.
The embodiments of FIGURES 13 and 14 may be sold together in a container. Frequently replaced components, such as the bllshings 418, fasteners 436 and 470, and dowel 401, may be sold together or separately in a replacement kit or kits.
FIGURES 15 and 16 show an alternate embodiment of the housing 524 that includes cylinders 512 and stem 516. The stem 516 of the embodiment shown in FIGURES 15 and 16, may define a recess 517 that can be used for a logo or emblem.
The foregoing description is for purposes of illustration only and 20 is not intended to limit the scope of protection accorded this invention. Thescope of protection is to be measured by the following claims, which should be interpreted as broadly as the inventive contribution permits.
Claims (65)
1. A stabilizer link comprising:
a) a cylinder defining a pair of contiguous bores opening in opposite directions, the pair of bores defining an axis;
b) a stem associated with the cylinder for mounting the cylinder on a vehicle;
c) a pair of bushings, each bushing received into a respective bore, each bushing defining a channel;
d) a shaft received into the channels of the pair of bushings;
and e) at least one fastening element for securing the shaft within the channels of the pair of bushings.
a) a cylinder defining a pair of contiguous bores opening in opposite directions, the pair of bores defining an axis;
b) a stem associated with the cylinder for mounting the cylinder on a vehicle;
c) a pair of bushings, each bushing received into a respective bore, each bushing defining a channel;
d) a shaft received into the channels of the pair of bushings;
and e) at least one fastening element for securing the shaft within the channels of the pair of bushings.
2. The stabilizer link of claim 1 wherein the fastening element comprises a distal retainer abutting a respective bushing.
3. The stabilizer link of claim 2 wherein the distal retainer and the shaft are unitary.
4. The stabilizer link of claim 3 wherein the distal retainer and the shaft are integral.
5. The stabilizer link of claim 2 wherein the distal retainer comprises a distal ring having a first flat surface that abuts the respective bushing and a circumferential flange angled with respect to the first flat surface.
6. The stabilizer link of claim 1 wherein the shaft includes a proximal end and the fastening element comprises a proximal retainer abutting a respective bushing and a fastener engaged with the proximal end.
7. The stabilizer link of claim 6 wherein the fastener and the proximal retainer are unitary.
8. The stabilizer link of claim 7 wherein the fastener and the proximal retainer are integral.
9. The stabilizer link of claim 6 wherein the fastener and the proximal end are threaded.
10. The stabilizer link of claim 6 wherein the proximal retainer comprises a proximal ring disposed about the shaft.
11. The stabilizer link of claim 6 wherein the proximal end of the shaft is threaded and wherein the fastener and the proximal retainer are unitary, and the fastener includes a plurality of parallel engaging fingers extending away from the respective bushing, the fingers having inwardly-facing threaded walls for engaging the threaded proximal end of the shaft.
12. The stabilizer link of claim 6 wherein the proximal retainer comprises a proximal ring having a second flat surface that abuts the respective bushing and a circumferential flange angled with respect to the second flat surface.
13. The stabilizer link of claim 1 wherein each bore tapers outward in a direction opposite its contiguous bore, each bushing being matingly received into its respective bore.
14. The stabilizer link of claim 13 wherein the bushings are tapered to complement the tapered bores defined by the cylinder.
15. The stabilizer link of claim 14 wherein each channel is substantially cylindrical along a length of its respective bushing and each bushing includes a pair of parallel flat ends and first and second frustoconicalouter bushing walls with tapers that narrow toward the bushing flat ends, the first outer bushing wall extending along most of the length of the bushing and being matingly received by its respective bore, the second outer bushing wall extending at least partially beyond its respective bore, the flat ends of the bushings being substantially perpendicular to the axes of the bores.
16. The stabilizer link of claim 14 wherein the bushings are constructed of polyurethane with a hardness of about 85 to about 95 durometers.
17. The stabilizer link of claim 1 wherein the cylinder includes a tapered inner wall that defines the pair of tapered bores and a central ridge dividing the bores, the inner wall being configured to limit the axial movement of the bushings.
18. A stabilizer link comprising:
a) a pair of hollow cylinders spaced apart from each other, each cylinder including a pair of open ends;
b) a stem joining the cylinders;
c) a pair of bushing configurations, each bushing configuration having two ends separated by a length and being received substantially within a respective cylinder, each bushing configuration defining a channel;
d) two shafts, each shaft having a distal end and a proximal end and received into the channel of a respective bushing configuration;
e) a pair of distal retainers, each distal retainer and a respective shaft being unitary and each distal retainer including a first portion facing one end of the respective bushing configuration;
f) a pair of fasteners for securing the shafts within the channels of the respective bushing configurations; and g) a pair of proximal retainers, each proximal retainer and a respective fastener being unitary and each proximal retainer-including a second portion facing the other end of the respective bushing configuration.
a) a pair of hollow cylinders spaced apart from each other, each cylinder including a pair of open ends;
b) a stem joining the cylinders;
c) a pair of bushing configurations, each bushing configuration having two ends separated by a length and being received substantially within a respective cylinder, each bushing configuration defining a channel;
d) two shafts, each shaft having a distal end and a proximal end and received into the channel of a respective bushing configuration;
e) a pair of distal retainers, each distal retainer and a respective shaft being unitary and each distal retainer including a first portion facing one end of the respective bushing configuration;
f) a pair of fasteners for securing the shafts within the channels of the respective bushing configurations; and g) a pair of proximal retainers, each proximal retainer and a respective fastener being unitary and each proximal retainer-including a second portion facing the other end of the respective bushing configuration.
19. The stabilizer link of claim 18 wherein each distal retainer and the respective shaft are integral.
20. The stabilizer link of claim 18 wherein each proximal retainer and the respective fastener are integral.
21. The stabilizer link of claim 18 wherein the distal and proximal retainers are located outside the cylinders and channels.
22. The stabilizer link of claim 18 wherein the proximal ends of the shaft are threaded and wherein each fastener includes a threaded inner wall that defines a hole for receiving the threaded proximal end of the respective shaft and engages the threaded proximal end.
23. The stabilizer link of claim 18 whereineach distal retainer comprises a distal ring disposed about the respective shaft and each proximal retainer comprises a proximal ring disposed about the respective shaft.
24. The stabilizer link of claim 23 wherein each first and second portion includes a generally flat surface and a circumferential flange angled with respect to the flat surface, the flat surface of each distal ring facing the flat surface of a respective proximal ring with the circumferential flanges of respective distal and proximal rings extending away from each other.
25. The stabilizer link of claim 18 wherein each cylinder defines a pair of contiguous bores opening in opposite directions and each bushing configuration includes two bushings, each bushing received into a respective bore.
26. The stabilizer link of claim 25 wherein each bore tapers in a direction opposite its contiguous bore and the bushings are tapered to complement the tapered bores, and wherein each cylinder includes a tapered inner wall that defines one of the pairs of tapered bores and a central ridge dividing the bores, the tapered inner walls configured to limit the axial movement of the bushings
27. A replacement kit for a stabilizer link that has a pair of cylinders, each cylinder defining a pair of contiguous tapered bores opening in opposite directions, each bore having an axis; a stem joining the cylinders; andtwo shafts, each received into a respective pair of bores; the kit comprising:
a) two pairs of bushings, each bushing configured to be matingly received into a respective bore, each bushing defining a generally cylindrical channel and the channels of each pair of bushings configured to receive a respective shaft;
b) a pair of fasteners for retaining the bushings within the bores, each fastener configured to engage the respective shaft to secure the respective shaft within a respective pair of channels;
c) a pair of retainers, each retainer configured to abut a respective bushing and being unitary with a respective fastener; and d) a container that retains the bushings, fasteners and retainers.
a) two pairs of bushings, each bushing configured to be matingly received into a respective bore, each bushing defining a generally cylindrical channel and the channels of each pair of bushings configured to receive a respective shaft;
b) a pair of fasteners for retaining the bushings within the bores, each fastener configured to engage the respective shaft to secure the respective shaft within a respective pair of channels;
c) a pair of retainers, each retainer configured to abut a respective bushing and being unitary with a respective fastener; and d) a container that retains the bushings, fasteners and retainers.
28. The replacement kit of claim 27 wherein each retainer is integral with the respective fastener.
29. The replacement kit of claim 27 wherein each retainer comprises a ring configured to be disposed about a respective shaft.
30. The replacement kit of claim 27 wherein each fastener includes a threaded inner wall that defines a hole for receiving a threaded end of the respective shaft to engage the threaded end.
31. The replacement kit of claim 30 further including a pair of cotter pins engageable with the fasteners for securing the fasteners to the threaded ends, the container also retaining the pair of cotter pins.
32. The replacement kit of claim 27 wherein each retainer includes a generally flat surface and a circumferential flange angled with respect to the flat surface.
33. The replacement kit of claim 32 wherein the circumferential flange of each retainer is configured to extend away from the respective bushing at an angle with respect to its flat surface of about 30 degrees.
34. The replacement kit of claim 27 wherein each fastener further includes a plurality of parallel engaging fingers extending from the respective retainer, the fingers having inwardly-facing threaded walls configured to engage a threaded proximal end of the respective shaft.
35. The replacement kit of claim 27 wherein the bushings are substantially the same in configuration and material.
36. The stabilizer link of claim 1 wherein each bushing has a pair of ends, and the fastening element includes a pair of washers disposed about the shaft and located outside of the bores and channels, each bushing being in abutting engagement with a respective washer.
37. The stabilizer link of claim 36 wherein each washer includes a flat portion and a circumferential flange angled with respect to the flat portion.
38. The stabilizer link of claim 36 wherein the shaft has a proximal threaded end, and the fastening element further includes a nut engageable with the proximal threaded end and being in abutting engagement with a respective washer.
39. The stabilizer link of claim 38 wherein a cotter pin hole is defined in the threaded end, and the nut is a castle nut; and wherein the fastening element further includes a cotter pin for securing the castle nut to the threaded end.
40. A replacement kit for a stabilizer link that has a cylinder defining a pair of contiguous tapered bores opening in opposite directions, each bore having an axis; a stem associated with the cylinder for mounting the cylinder on a vehicle; and a shaft received into the pair of bores; the kit comprising:
a) a pair of bushings, each bushing configured to be matingly received into one of the respective bores, each bushing defining a generally cylindrical channel, and the channels of the pair of bushings are configured to receive the shaft;
b) a fastener for retaining the bushings within the bores, the fastener configured to engage the shaft to secure the shaft within the channels;
c) a retainer configured to abut one of the respective bushings and being unitary with the fastener; and d) a container that retains the bushings, fastener, and retainer.
a) a pair of bushings, each bushing configured to be matingly received into one of the respective bores, each bushing defining a generally cylindrical channel, and the channels of the pair of bushings are configured to receive the shaft;
b) a fastener for retaining the bushings within the bores, the fastener configured to engage the shaft to secure the shaft within the channels;
c) a retainer configured to abut one of the respective bushings and being unitary with the fastener; and d) a container that retains the bushings, fastener, and retainer.
41. The replacement kit of claim 40 wherein the retainer is integral with the fastener.
42. The replacement kit of claim 40 wherein the retainer comprises a ring configured to be disposed about the shaft.
43. The replacement kit of claim 40 wherein the fastener includes a threaded inner wall that defines a hole for receiving a threaded end of the shaft to engage the threaded end.
44. The replacement kit of claim 43 further including a cotter pin engageable with the fastener for securing the fastener to the threaded end, the container also retaining the cotter pin.
45. The replacement kit of claim 40 wherein the retainer includes a generally flat surface and a circumferential flange angled with respect to the flat surface.
46. The replacement kit of claim 45 wherein the circumferential flange of the retainer is angled with respect to its flat surface about 30 degrees.
47. The replacement kit of claim 40 wherein the fastener further includes a plurality of parallel engaging fingers extending from the retainer, the fingers having inwardly-facing threaded walls configured to engage a threaded proximal end of the shaft.
48. The replacement kit of claim 40 wherein the bushings are substantially the same in configuration and material.
49. A method of assembling a stabilizer link for mounting to a vehicle comprising:
a) providing a cylinder defining a pair of contiguous bores opening in opposite directions, the pair of bores defining an axis;
b) inserting a pair of bushings into respective bores, each bushing defining a channel, the channels being substantially coaxial with the axis of the cylinder;
c) providing a shaft having a distal end and a proximal end;
d) providing a distal retainer adjacent to the distal end of the shaft;
e) sliding the shaft through the channels of the bushings so that the distal retainer abuts a respective bushing;
f) providing a proximal retainer at the proximal end of the shaft; and g) securing a fastening element to the proximal end of the shaft for retaining the shaft within the channels of the bushings.
a) providing a cylinder defining a pair of contiguous bores opening in opposite directions, the pair of bores defining an axis;
b) inserting a pair of bushings into respective bores, each bushing defining a channel, the channels being substantially coaxial with the axis of the cylinder;
c) providing a shaft having a distal end and a proximal end;
d) providing a distal retainer adjacent to the distal end of the shaft;
e) sliding the shaft through the channels of the bushings so that the distal retainer abuts a respective bushing;
f) providing a proximal retainer at the proximal end of the shaft; and g) securing a fastening element to the proximal end of the shaft for retaining the shaft within the channels of the bushings.
50. The method of claim 49 including providing the shaft unitarily with the distal retainer.
51. The method of claim 49 including providing the proximal retainer unitarily with the fastening element.
52. A link for mounting to a component of a vehicle, the component defining a mounting hole; the link comprising:
a) a hollow cylinder including a pair of open ends;
b) a stem associated with the cylinder for mounting the cylinder to the vehicle;
c) a bushing configuration having two ends separated by a length and being received substantially within the cylinder, the bushing configuration defining a channel;
d) a shaft having a distal end and a proximal end and received into the channel of the bushing configuration for mounting the link to the component of the vehicle through the mounting hole;
e) a hollow cylindrical dowel associated with the shaft and the mounting hole and configured to be accepted into the mounting hole and on the shaft; and f) at least one fastening element for securing the shaft within the channel of the bushing configuration.
a) a hollow cylinder including a pair of open ends;
b) a stem associated with the cylinder for mounting the cylinder to the vehicle;
c) a bushing configuration having two ends separated by a length and being received substantially within the cylinder, the bushing configuration defining a channel;
d) a shaft having a distal end and a proximal end and received into the channel of the bushing configuration for mounting the link to the component of the vehicle through the mounting hole;
e) a hollow cylindrical dowel associated with the shaft and the mounting hole and configured to be accepted into the mounting hole and on the shaft; and f) at least one fastening element for securing the shaft within the channel of the bushing configuration.
53. The link of claim 52 including a distal fastener for securing the link to the vehicle.
54. The link of claim 52 wherein the fastening element comprises a proximal retainer unitary with the shaft.
55. The link of claim 54 wherein the proximal retainer and the shaft are integral.
56. The link of claim 54 including a distal fastener for securing the shaft within the channel of the bushing configuration.
57. The link of claim 56 wherein the distal fastener also secures the shaft to the component of the vehicle.
58. The link of claim 52 including a distal retainer abutting one end of the bushing configuration.
59. The link of claim 58 wherein the distal retainer and the shaft are unitary.
60. The link of claim 59 wherein the distal retainer and the shaft are integral.
61. The link of claim 58 wherein the distal retainer comprises a distal ring disposed about the shaft.
62. The link of claim 59 wherein the distal retainer defines a circumferential groove facing away from the bushing configuration.
63. The link of claim 52 wherein the dowel defines a substantially right cylindrical inner surface for receiving the shaft and a frustoconical outer surface adapted for mating engagement with the mounting hole.
64. The link of claim 63 wherein the shaft includes a substantially cylindrical mounting portion.
65. The link of claim 52 wherein the dowel defines a substantially longitudinal slot such that the diameter of the dowel is variable. 66. The link of claim 58 further comprising a washer disposed about the shaft and located between the distal retainer and the component of the vehicle.
67. The link of claim 66 wherein the washer includes a flat portion and a circumferential flange angled with respect to the flat portion.
68. The link of claim 67 wherein the flange angles toward the distal retainer.
69. A replacement kit for a link; the link having a cylinder defining a pair of contiguous tapered bores opening in opposite directions, each bore having an axis; a stem associated with the cylinder for mounting the cylinder on a vehicle; and a shaft received into the pair of bores; the kit comprising:
a) a pair of bushings, each bushing configured to be matingly received into one of the respective bores, each bushing defining a generally cylindrical channel, the channels of the pair of bushings configured to receive the shaft;
b) a fastener for retaining the bushings within the bores, the fastener configured to engage the shaft to secure the shaft within the channels;
c) a hollow cylindrical dowel defining a substantially right cylindrical inner surface for receiving the shaft and defining a frustoconical outer surface configured to complement a mounting hole defined by the vehicle; and d) a container that retains the bushings, fastener, and dowel.
70. The kit of claim 69 further comprising a washer including a flat portion and a circumferential flange angled with respect to the flat portion.
71. The kit of claim 69 wherein the dowel defines a substantially longitudinal slot such that the diameter of the dowel is variable.72. A method of assembling a link for mounting to a vehicle comprising:
a) providing a cylinder defining a pair of contiguous bores opening in opposite directions, the pair of bores defining an axis;
b) inserting a pair of bushings into respective bores, each bushing defining a channel, the channels being substantially coaxial with the axis of the bores;
c) providing a shaft having a distal end and a proximal end;
d) providing a hollow cylindrical dowel defining a substantially right cylindrical inner surface for receiving the shaft and a frustoconical outer surface configured to complement a mounting hole defined by the vehicle;
e) sliding the shaft through the channels of the bushings;
f) providing a proximal retainer at the proximal end of the shaft;
g) securing a fastening element to the proximal end of the shaft for retaining the shaft within the channels of the bushings;
h) inserting the hollow cylindrical dowel into the mounting hole of the vehicle;
i) sliding the distal end of the shaft through the dowel; and j) securing a fastening element to the distal end of the shaft for retaining the shaft within the mounting hole.
73. The method of claim 72 including providing a washer disposed about the shaft and located between the distal retainer and a component of the vehicle.
67. The link of claim 66 wherein the washer includes a flat portion and a circumferential flange angled with respect to the flat portion.
68. The link of claim 67 wherein the flange angles toward the distal retainer.
69. A replacement kit for a link; the link having a cylinder defining a pair of contiguous tapered bores opening in opposite directions, each bore having an axis; a stem associated with the cylinder for mounting the cylinder on a vehicle; and a shaft received into the pair of bores; the kit comprising:
a) a pair of bushings, each bushing configured to be matingly received into one of the respective bores, each bushing defining a generally cylindrical channel, the channels of the pair of bushings configured to receive the shaft;
b) a fastener for retaining the bushings within the bores, the fastener configured to engage the shaft to secure the shaft within the channels;
c) a hollow cylindrical dowel defining a substantially right cylindrical inner surface for receiving the shaft and defining a frustoconical outer surface configured to complement a mounting hole defined by the vehicle; and d) a container that retains the bushings, fastener, and dowel.
70. The kit of claim 69 further comprising a washer including a flat portion and a circumferential flange angled with respect to the flat portion.
71. The kit of claim 69 wherein the dowel defines a substantially longitudinal slot such that the diameter of the dowel is variable.72. A method of assembling a link for mounting to a vehicle comprising:
a) providing a cylinder defining a pair of contiguous bores opening in opposite directions, the pair of bores defining an axis;
b) inserting a pair of bushings into respective bores, each bushing defining a channel, the channels being substantially coaxial with the axis of the bores;
c) providing a shaft having a distal end and a proximal end;
d) providing a hollow cylindrical dowel defining a substantially right cylindrical inner surface for receiving the shaft and a frustoconical outer surface configured to complement a mounting hole defined by the vehicle;
e) sliding the shaft through the channels of the bushings;
f) providing a proximal retainer at the proximal end of the shaft;
g) securing a fastening element to the proximal end of the shaft for retaining the shaft within the channels of the bushings;
h) inserting the hollow cylindrical dowel into the mounting hole of the vehicle;
i) sliding the distal end of the shaft through the dowel; and j) securing a fastening element to the distal end of the shaft for retaining the shaft within the mounting hole.
73. The method of claim 72 including providing a washer disposed about the shaft and located between the distal retainer and a component of the vehicle.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US08/708,356 US5794965A (en) | 1995-06-23 | 1996-09-04 | Stabilizer link |
| US08/708,356 | 1996-09-04 | ||
| US08/880,122 | 1997-06-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2210331A1 true CA2210331A1 (en) | 1998-03-04 |
Family
ID=24845480
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2210331 Abandoned CA2210331A1 (en) | 1996-09-04 | 1997-07-22 | Stabilizer link |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2210331A1 (en) |
-
1997
- 1997-07-22 CA CA 2210331 patent/CA2210331A1/en not_active Abandoned
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| Date | Code | Title | Description |
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| EEER | Examination request | ||
| FZDE | Dead |