SUSPENSION ASSEMBLY FOR A CYCLE HAVING A FORK ARM WITH DUAL OPPOSING TAPERS

Abstract

A multi-bar suspension assembly for a cycle having improved stability includes a first arm having a first arm fixed pivot and a first arm shock pivot. The first arm includes a hollow internal portion having first end and a second end that are both wider than a narrow intermediate portion. A shock link has a shock link fixed pivot and a shock link floating pivot. A shock absorber has a first shock mount and a second shock mount. A wheel carrier has a wheel carrier first pivot and a wheel carrier second pivot spaced apart from one another, and a wheel mount that is adapted to be connected to a wheel. A control link has a control link floating pivot and a control link fixed pivot, the control link floating pivot being pivotably connected to the wheel carrier second pivot, and the control link fixed pivot being pivotably connected to the first arm control pivot.

Description

INCORPORATION BY REFERENCE TO ANY PRIORITY APPLICATIONS

Any and all applications for which a foreign or domestic priority claim is identified in the Application Data Sheet as filed with the present application are hereby incorporated by reference under 37 CFR 1.57.

FIELD OF THE INVENTION

The disclosure is generally directed to cycles, and more specifically directed to cycles having a suspension assembly having a fork arm with dual opposing tapers.

BACKGROUND

Recently, telescopic front suspension forks have dominated suspension systems for two-wheeled vehicles. A telescopic fork includes sliding stantions connected in a steerable manner to a cycle frame, and at the same time, includes a telescoping mechanism for wheel displacement. Sliding stantions require very tight manufacturing tolerances, so expensive round centerless ground stantions are almost always used in high performance telescopic forks. Outer surfaces of the stantion typically slide against bushings to allow for compliance, and in many designs, the inner surfaces of the stantions slide against a damper or air spring piston to absorb shocks.

Front suspension for a cycle is subject to large bending forces fore and aft and less significant lateral forces. The typically round stantions in a telescopic fork must be sized to support the greatest loads encountered by the suspension during operation, which are typically in the fore/aft direction. This requires the use of large section or diameter stantions. The larger the stantions, the greater the area of the supporting bushings and sliding surfaces. Because of the stacked layout, multiple redundant sliding surfaces must be used to seal in oil and air, as well as provide ample structural support.

Because telescopic forks have relatively large stantions, and relatively large siding surfaces and seals, large breakaway friction in the system (known as stiction) is generated by these components. Stiction resists compression of the suspension in reaction to bumps, which is a drawback in a suspension product where the goal is to react to road conditions, for example by deflecting in response to ground conditions, and/or absorbing impact from bumps. Additionally, as the telescopic fork is loaded in the fore/aft direction (usually on impact or braking), the bushings bind, resulting in even greater stiction at the exact moment when a rider needs the most compliance.

Additionally, in the telescopic fork, mechanical trail is constrained. Another problem with telescopic fork architecture is that when they are installed, mechanical trail reduces as the suspension is compressed, which reduces stability. When mechanical trail reduces, as the suspension compresses, less torque is required to steer the front wheel, causing a feeling of instability. This instability is a flaw in the telescopic fork. However, because most riders of 2-wheeled vehicles grew up only riding telescopic forks, they only know this feeling and nothing else. Thus, the inherent instability of a telescopic fork is the accepted normal.

SUMMARY

In accordance with one exemplary aspect, a suspension assembly for a cycle includes a fork having a first arm including a wall defining a hollow internal portion of the first arm. A plurality of interconnected links is operatively connected to the first arm. A shock absorber is at least partially disposed in the hollow internal portion. The hollow internal portion of the first arm has first end and a second end that are both wider than a narrow intermediate portion.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a side view of a cycle including a front wheel suspension assembly constructed according to the teachings of the disclosure.

FIG. 1B is a side view of an alternate embodiment of a cycle including a front wheel suspension assembly constructed according to the teachings of the disclosure, the cycle of FIG. 1B including a rear wheel suspension assembly.

FIG. 2A is a close up side view of the front wheel suspension assembly of FIG. 1A or 1B in an uncompressed state.

FIG. 2B is a close up side view of the front wheel suspension assembly of FIG. 1A or 1B in a compressed state.

FIG. 3 is a side exploded view of the front wheel suspension assembly of FIGS. 2A and 2B.

FIGS. 4A-4W are side cross-sectional views of alternate embodiments of a fork arm of the suspension assembly of FIGS. 1-3.

DETAILED DESCRIPTION

The present invention is not to be limited in scope by the specific embodiments described below, which are intended as exemplary illustrations of individual aspects of the invention. Functionally equivalent methods and components fall within the scope of the invention. Indeed, various modifications of the invention, in addition to those shown and described herein, will become apparent to those skilled in the art from the foregoing description. Such modifications are intended to fall within the scope of the appended claims. Throughout this application, the singular includes the plural and the plural includes the singular, unless indicated otherwise. All cited publications, patents, and patent applications are herein incorporated by reference in their entirety.

Turning now to FIG. 1A, a cycle 10 includes a frame 12, a front wheel 14 rotatably connected to a fork 30, which can be bifurcated or single sided, and a rear wheel 16 rotatably connected to the frame 12. The rear wheel 16 is drivable by a drive mechanism, such as a chain 18 connected to a wheel sprocket 20 and to a chainring 22, so that driving force may be imparted to the rear wheel 16. The fork 30, allows the front wheel 14 to deflect in response to ground conditions as a rider rides the cycle and to improve handling and control during riding. To improve handling characteristics, the fork 30 and the front wheel 14 is operatively connected to a suspension assembly 46. The frame 12 may optionally include a rear wheel suspension assembly (not shown in FIG. 1A), which may allow the rear wheel 16 to deflect in response to ground conditions as a rider rides the cycle and to improve handling and control during riding.

Turning now to FIG. 1B, a cycle 10 includes a frame 12, a front wheel 14 rotatably connected to a fork 30, which can be bifurcated or single sided, and a rear wheel 16 rotatably connected to the frame 12. The fork 30 and the front wheel 14 may be operatively connected to the suspension assembly 46. The rear wheel 16 is drivable by a drive mechanism, such as a chain 18 connected to a wheel sprocket 20 and to a chainring 22, so that driving force may be imparted to the rear wheel 16. The suspension assembly 46 allows the front wheel 14 to deflect in response to ground conditions as a rider rides the cycle and to improve handling and control during riding. The frame 12 may optionally include a rear wheel suspension assembly 24, which may allow the rear wheel 16 to deflect in response to ground conditions as a rider rides the cycle and to improve handling and control during riding.

As illustrated in FIGS. 2A, 2B, and 3, the fork 30 includes a first arm 32 operatively connected to a steering shaft 34. The steering shaft 34 includes a steering axis S that is formed by a central axis of the steering shaft 34. The first arm 32 has a first end 36 and a second end 38 and a hollow interior, the first arm 32 including a first arm fixed pivot 40 and a first arm shock pivot 42. The first arm shock pivot 42 operably connects a suspension device, such as a shock absorber 44 to the first arm 32. For example, the first arm shock pivot 42 allows relative motion, in this case rotation, between the shock absorber 44 and the first arm 32. In other embodiments, other types of relative motion, such as flexure or translation, between the shock absorber 44 and the first arm 32 may be employed. The first arm fixed pivot 40 pivotably connects one element of the suspension assembly 46, as discussed further below, to the first arm 32.

A shock link 50 is pivotably connected to the first arm fixed pivot 40. The shock link 50 includes a shock link fixed pivot 52 and a shock link floating pivot 54 spaced apart from one another along a length of the shock link 50. The shock link 50 is pivotably connected to the first arm fixed pivot 40 at the shock link fixed pivot 52 such that the shock link 50 is rotatable about the shock link fixed pivot 52 and the shock link fixed pivot 52 remains in a fixed location relative to the first arm 32, while the shock link floating pivot 54 is movable relative to the first arm 32.

A pivot, as used herein, includes any connection structure that may be used to operatively connect one element to another element, and that allows relative movement between the connected elements. An operative connection may allow for one component to move in relation to another while constraining movement in one or more degrees of freedom. For example, the one degree of freedom may be pivoting about an axis. In one embodiment, a pivot may be formed from a journal or through hole in one component and an axle in another component. In other examples, pivots may include ball and socket joints. Yet other examples of pivots include, but are not limited to singular embodiments and combinations of, compliant mounts, sandwich style mounts, post mounts, bushings, bearings, ball bearings, plain bearings, flexible couplings, flexure pivots, journals, holes, pins, bolts, and other fasteners. Also, as used herein, a fixed pivot is defined as a pivotable structure that does not change position relative the first arm 32. As used herein, a floating pivot is defined as a pivot that is movable (or changes position) relative to another element, and in this case, is movable relative to first arm 32.

In the disclosed embodiment, the suspension assembly 46 is configured in a trailing orientation. A trailing orientation is defined herein as a linkage that includes a fixed pivot that is forward of the corresponding floating pivot when the cycle is traveling in the forward direction of travel as represented by arrow A in FIGS. 1A and 1B. In other words, the floating pivot trails the fixed pivot when the cycle is traveling in the forward direction of travel. For example, in the illustrated embodiment, the shock link fixed pivot 52 is forward of the shock link floating pivot 54, similarly, in the illustrated embodiment, the control link fixed pivot 74 is forward of the control link floating pivot 72. The disclosed suspension assembly or suspension assembly 46 is also characterized as a multi-bar linkage. A multi-bar linkage is defined herein as a linkage in which any part of the front wheel 14 is directly connected to a link that is not directly connected to the fork 30. In other embodiments, the disclosed fork arms may be used in a leading link suspension assembly.

The shock absorber 44 includes a first shock mount 56 and a second shock mount 58, the first shock mount 56 being pivotably connected to the first arm shock pivot 42, the second shock mount 58 being pivotably connected to a shock connection pivot 60 located between the shock link fixed pivot 52 and the shock link floating pivot 54 along a length of the shock link 50.

A wheel carrier 62 includes a wheel carrier first pivot 64 and a wheel carrier second pivot 66 spaced apart from one another along a length of the wheel carrier 62. Both the wheel carrier first pivot 64 and the wheel carrier second pivot 66 are floating pivots, as they both move relative to the first arm 32. A wheel mount 68 is adapted to be connected to a center of a wheel, for example the front wheel 14. In the disclosed embodiment, a center of the front wheel 14 is rotatably connected to the wheel mount 68. The wheel carrier first pivot 64 is pivotably connected to the shock link floating pivot 54 so that the wheel carrier second pivot 66 is pivotable about the wheel carrier first pivot 64 relative to the shock link floating pivot 54.

A control link 70 includes a control link floating pivot 72 and a control link fixed pivot 74. The control link floating pivot 72 is pivotably connected to the wheel carrier second pivot 66, and the control link fixed pivot 74 is pivotably connected to a first arm control pivot 76 located on the first arm 32 such that the control link floating pivot 72 is pivotable about the control link fixed pivot 74, which remains in a fixed location relative to the first arm control pivot 76.

In some embodiments, the shock connection pivot 60 is closer to the shock link fixed pivot 52 than to the shock link floating pivot 54, as illustrated in FIGS. 2A, 2B, and 3. As a function of suspension compression and link movement, a perpendicular distance D between a central axis I of an inshaft 80 of the shock absorber 44 and a center of the shock link fixed pivot 52 varies as the shock absorber 44 is compressed and extended, as the shock absorber pivots about the first shock mount 56. This pivoting and varying of the perpendicular distance D allows the leverage ratio and motion ratio to vary as the shock absorber 44 compresses and extends. As a function of suspension compression and link movement, a mechanical trail distance T varies as the shock absorber 44 compresses and extends. The mechanical trail distance T is defined as the perpendicular distance between the steering axis S and the contact point 82 of the front wheel 14 with the ground 84. More specifically, as the suspension compresses, beginning at a state of full extension, the mechanical trail distance T increases, thus increasing stability during compression. Compression is usually experienced during braking, cornering, and shock absorbing, all of which benefit from increased stability that results from the mechanical trail distance increase.

Mechanical trail (or “trail”, or “caster”) is an important metric relating to handling characteristics of two-wheeled cycles. Mechanical trail is a configuration in which a wheel is rotatably attached to a fork that is connected to a steering shaft 34, which has a steering axis that is offset from the contact point of the wheel with the ground. When the steering axis is forward of the contact point, as in the case of a shopping cart, this configuration allows the caster wheel to follow the direction of cart travel. If the contact point moves forward of the steering axis (for example when reversing direction of a shopping cart), the directional control becomes unstable and the wheel spins around to the original position in which the contact point trails the steering axis. The friction between the ground and the wheel causes a self-righting torque that tends to force the wheel to trail the steering axis. The greater the distance between the contact point and perpendicular to the steering axis, the more torque is generated, and the greater the stability of the system. Conversely, the shorter the distance between the cycle wheel contact point and perpendicular to the steering axis, the less torque is generated, and the lower the stability of the system.

This caster effect is an important design characteristic in cycles. Generally, the caster effect describes the cycle rider's perception of stability resulting from the mechanical trail distance described above. If the wheel gets out of line, a self-aligning torque automatically causes the wheel to follow the steering axis again due to the orientation of the wheel ground contact point being behind the steering axis of the fork. As the contact point of the wheel with the ground is moved further behind the steering axis, self aligning torque increases. This increase in stability is referred to herein as the caster effect.

In the disclosed wheel suspension assembly, when the suspension is at a state of full extension as shown in FIG. 2A, the steering axis of the fork 30 projects ahead of the contact point 82. As the suspension assembly compresses (e.g., FIG. 2B), the steering axis S projects farther ahead of the contact point 82, which results in an increase in mechanical trail distance T and thus, an increase in stability. This increased stability stands in contrast to known telescopic fork cycles, which experience reduced trail and thus reduced stability during compression.

Leverage ratios or motion ratios are important metrics relating to performance characteristics of some suspensions. In certain embodiments, a shock absorber can be compressed at a constant or variable rate as the suspension moves towards a state of full compression. As a wheel is compressed, incremental suspension compression distance measurements are taken. Incremental suspension compression distance is measured from the center of the wheel at the wheel rotation axis and parallel with the steering axis, starting from a state of full suspension extension, and moving towards a state of full suspension compression. These incremental measurements are called the incremental suspension compression distance. A shock absorber length can be changed by shock link, and/or control link, and/or wheel carrier movements as the suspension compresses. At each incremental suspension compression distance measurement, a shock absorber length measurement is taken. The relationship between incremental suspension compression distance change and shock absorber length change for correlating measurements of the suspension's compression is called leverage ratio or motion ratio. Leverage ratio and motion ratio are effectively equivalent but mathematically different methods of quantifying the effects of variable suspension compression distance versus shock compression distance. Overall leverage ratio is the average leverage ratio across the entire range of compression. Overall leverage ratio can be calculated by dividing the total suspension compression distance by the total shock absorber compression distance. Overall motion ratio is the average motion ratio across the entire range of compression. Overall motion ratio can be calculated by dividing the total shock absorber compression distance by the total suspension compression distance.

Generally, a suspended wheel has a compressible wheel suspension travel distance that features a beginning travel state where the suspension is completely uncompressed to a state where no further suspension extension can take place, and an end travel state where a suspension is completely compressed to a state where no further suspension compression can take place. At the beginning of the wheel suspension travel distance, when the suspension is in a completely uncompressed state, the shock absorber is in a state of least compression, and the suspension is easily compressed. As the suspended wheel moves compressively, force at the wheel changes in relation to shock absorber force multiplied by a leverage ratio.

In known telescopic forks no leverage ratio exists and, the leverage ratio is always equivalent to 1:1 due to the direct coupling of the wheel to the shock absorber.

A leverage ratio curve is a graphed quantifiable representation of leverage ratio versus wheel compression distance or percentage of full compression distance. Wheel compression distance, suspension compression, or wheel travel is measured from the center of the wheel at the wheel rotation axis and parallel with the steering axis, with the initial 0 percent measurement taken at full suspension extension with the vehicle (or cycle) unladen. As a suspension is compressed from a state of full extension to a state of full compression at a constant rate, measurements of shock absorber length are taken as the shortest distance between a first shock pivot and a second shock pivot at equal increments of suspension compression. When graphed as a curve on a Cartesian graph, leverage ratio is shown on the Y axis escalating from the x axis in a positive direction, and vertical wheel travel is shown on the X axis escalating from the Y axis in a positive direction.

A motion ratio curve is a graphed quantifiable representation of motion ratio versus wheel compression distance or percentage of full compression distance. Wheel compression distance, suspension compression, or wheel travel is measured from the center of the wheel at the wheel rotation axis and parallel with the steering axis, with the initial 0 percent measurement taken at full suspension extension with the vehicle (or cycle) unladen. As a suspension is compressed from a state of full extension to a state of full compression, measurements of shock absorber length are taken as the shortest distance between a first shock pivot and a second shock pivot at equal increments of suspension compression. When graphed as a curve on a Cartesian graph, motion ratio is shown on the Y axis escalating from the x axis in a positive direction, and vertical wheel travel is shown on the X axis escalating from the Y axis in a positive direction.

In certain embodiments, a leverage ratio or motion ratio curve can be broken down into three equal parts in relation to wheel compression distance or vertical wheel travel, a beginning 1/3 (third), a middle 1/3, and an end 1/3. In certain embodiments, a beginning 1/3 can comprise a positive slope, zero slope, and or a negative slope. In certain embodiments, a middle 1/3 can comprise a positive slope, zero slope, and or a negative slope. In certain embodiments, an end 1/3 can comprise a positive slope, zero slope, and or a negative slope. Certain preferred leverage ratio embodiments can comprise a beginning 1/3 with a positive slope, a middle 1/3 with a less positive slope, and an end 1/3 with a more positive slope. Certain preferred leverage ratio embodiments can comprise a beginning 1/3 with a negative slope, a middle 1/3 with negative and zero slope, and an end 1/3 with a positive slope. Certain preferred leverage ratio embodiments can comprise a beginning 1/3 with a positive and negative slope, a middle 1/3 with negative and zero slope, and an end 1/3 with a positive slope. Certain preferred leverage ratio embodiments can comprise a beginning 1/3 with a positive and negative slope, a middle 1/3 with negative and zero slope, and an end 1/3 with a more negative slope. Certain preferred motion ratio embodiments can comprise a beginning 1/3 with a negative slope, a middle 1/3 with a less negative slope, and an end 1/3 with a more negative slope. Certain preferred motion ratio embodiments can comprise a beginning 1/3 with a positive slope, a middle 1/3 with positive and zero slope, and an end 1/3 with a negative slope. Certain preferred motion ratio embodiments can comprise a beginning 1/3 with a negative and positive slope, a middle 1/3 with positive and zero slope, and an end 1/3 with a negative slope. Certain preferred motion ratio embodiments can comprise a beginning 1/3 with a negative and positive slope, a middle 1/3 with positive and zero slope, and an end 1/3 with a more positive slope.

In contrast to telescopic suspensions, the disclosed wheel suspension assembly provides a greater than 1:1 overall leverage ratio between the shock absorber 44 and the shock link 50, due to the indirect coupling (through the suspension assembly 46) of the wheel 14 and the shock absorber 44. In contrast to telescopic suspensions, the disclosed wheel suspension assembly provides a less than 1:1 overall motion ratio between the shock absorber 44 and the shock link 50, due to the indirect coupling (through the suspension assembly 46) of the wheel 14 and the shock absorber 44. Additionally, because of the movement arcs of the various linkage elements, at any given point during compression, instantaneous leverage ratio and motion ratio can vary non-linearly.

The central axis I of the inshaft 80 of the shock absorber 44 is arranged to form an angle B of between 0° and 20° relative to a central axis F of the first arm 32, the central axis F of the first arm 32 being defined by a line formed between the first arm shock pivot 42 and the first arm fixed pivot 40. In other embodiments, the central axis I of the inshaft 80 of the shock absorber 44 forms an angle with the central axis F of the first arm 32 of between 0° and 15°. In other embodiments, the central axis I of the inshaft 80 of the shock absorber 44 forms an angle with the central axis F of the first arm 32 of between 0° and 30°. The angle B may vary within these ranges during compression and extension.

The first arm 32 includes a hollow portion 86 and the shock absorber 44 is located at least partially within the hollow portion 86 of the first arm 32. As the shock absorber 44 pivots about the shock mount 56 when the suspension assembly 46 compresses and extends, clearance between the shock absorber 44 and the inner wall of the first arm 32 changes in the forward and aft direction (right and left in FIGS. 2A and 2B). More specifically, when the suspension assembly 46 is in a relatively uncompressed state, such as for example the uncompressed or fully extended state illustrated in FIG. 2A, the shock absorber 44 is positioned forward (in the direction of travel A) in the hollow portion 86 of the first arm 32 such that the shock absorber 44 has less clearance on a forward side (forward in the direction of travel A, to the right in FIGS. 2A and 2B) than on an aft side (opposite the direction of travel A, to the left in FIGS. 2A and 2B). As the suspension assembly compresses towards a partially compressed intermediate state, for example as illustrated in FIG. 2B, the shock absorber 44 swings or pivots aft (opposite the direction of travel A) so that the shock absorber 44 has less clearance on the aft side than on the forward side. This swinging or pivoting about the shock mount 56 is caused by movement of the shock link 50 as the suspension assembly 46 compresses. The hollow portion 86 of the first arm 32 flares outwardly (fore to aft) towards the bottom to accommodate this swinging or pivoting movement of the shock absorber 44.

The shock link fixed pivot 52 is offset forward of the central axis I of the inshaft 80 of the shock absorber 44. In other words, the central axis I of the inshaft 80 of the shock absorber 44 is positioned between the shock link fixed pivot 52 and the shock link floating pivot 54 in a plane defined by the central axis I of the inshaft 80, the shock link fixed pivot 52 and the shock link floating pivot 54 (i.e., the plane defined by the view of FIGS. 2A and 2B).

A line between the wheel carrier first pivot 64 and the wheel carrier second pivot 66 defines a wheel carrier axis WC, and the wheel mount 68 is offset from the wheel carrier axis WC in a plane defined by the wheel carrier axis WC and the wheel mount 68 (i.e., the plane defined by the view of FIG. 3). In some embodiments, the wheel mount 68 is offset from the wheel carrier axis WC towards the first arm 32, for example the embodiment illustrated in FIGS. 2A, 2B, and 3. In other embodiments, the wheel mount 68 may be offset from the wheel carrier axis WC away from the first arm 32. In yet other embodiments, the wheel mount 68 may be located on the wheel carrier axis WC.

In the embodiment of FIGS. 2A, 2B, and 3, the wheel mount 68 is located aft of the shock link fixed pivot 52, such that the central axis I of the inshaft 80 of the shock absorber 44 is located between the wheel mount 68 and the shock link fixed pivot 52 in a plane defined by the central axis I of the inshaft 80 of the shock absorber 44, the wheel mount 68 and the shock link fixed pivot 52 (i.e., the plane defined by the view of FIGS. 2A and 2B).

Turning now to FIG. 3, in some embodiments, the shock absorber 44 includes a shock body, in some embodiments comprising a spring 47 and damper having a shock body 87. The shock absorber 44 may further include the inshaft 80 that extends from the shock body 87. The second shock mount 58 is disposed at one end of the inshaft 80, and the inshaft 80 is pivotably connected to the shock connection pivot 60 by the second shock mount 58 such that the inshaft 80 is compressible and extendable relative to the shock body 87 as the shock link 50 pivots about the shock link fixed pivot 52.

The control link 70 is pivotably mounted to the first arm 32 at the first arm control pivot 76 that is located between the first arm fixed pivot 40 and the first arm shock pivot 42, along a length of the first arm 32.

Turning now to FIGS. 4A-W, multiple embodiments of a first arm 32 of the suspension assembly 46 of FIGS. 1-3 are illustrated. In the embodiments of FIGS. 4A-4W, like reference numbers are used to identify like parts. For example, in the embodiments of FIGS. 4A-4W, the first arm is referenced by numeral 32.

Each of the embodiments of the first arm 32 in FIGS. 4A-4W includes an internal space having a common dual opposing taper or hourglass design. More specifically, each of the embodiments of the first arm 32 of FIGS. 4A-4W includes a hollow internal portion 86, which at least partially houses the shock absorber 44, that is generally hourglass-shaped having a narrow intermediate portion and a wider first end 101 and a wider second end 102. The wider first and second ends 101, 102 are wider at least in the fore and aft direction (according to the direction of travel A defined above) than a narrow intermediate portion 103. In some embodiments, the first and second ends 101, 102 may be wider in the fore and aft direction and in a lateral direction (perpendicular to the direction of travel) than the narrow intermediate portion 103.

Because the first and second ends 101, 102, are wider than the narrow intermediate portion 103, the hollow internal portion 86 flares outwardly (e.g., gets larger) with respect to a central axis of the first arm 32 towards the first and second ends 101, 102. In other words, the hollow internal portion 86 flares outwardly at an angle A at the first end 101 and at an angle A′ at the second end 102. The angles A and A′ are positive and may or may not be equal to one another. Additionally, the angles A and A′ preferably fall in the range of 0.1 degrees to 30 degrees, for example 0.25 degrees to 20 degrees or 0.25 degrees to 10 degrees, and most preferably in the range of 0.25 degrees to 5 degrees, for example 0.5 degrees to 5 degrees or 1 degree to 5 degrees. Angles in the range of 0.1 degrees to 30 degrees, particularly 0.25 degrees to 5 degrees, provide enhanced strength, bending, and clearance characteristics that are particularly suited for a multi-bar cycle linkage. More specifically, angles in this range provide strong top sections of the first arm 32, good clearance for the shock absorber 44 to swing or pivot within the first arm 32, and targeted bending locations, that allow the first arm 32 to bend in the fore and aft directions, for superior ride performance.

In some embodiments illustrated in FIGS. 4A-4W, the first arm wall 104 may be linear in cross-section, the first arm wall 104 may have linear portions in cross-section, or the first arm wall 104 may be non-linear in cross-section.

The angle A for the outward taper of the upper end of the hollow inner portion 86 is defined in the forward direction when viewed in cross-section (FIGS. 4A-4W), by a first line 105 that begins on the forward side at the narrow intermediate location 103 and extends upward (towards the first arm shock pivot 42) such that the line 105 intersects the first arm wall 104 at the widest location of the hollow inner portion 86 between the narrow intermediate location 103 and the steering shaft 34 on the forward side. The angle A for the outward taper of the upper end of the hollow inner portion 86 is defined in the aft direction when viewed in cross-section (FIGS. 4A-4W), by a line 106 that begins on the aft side at the narrow intermediate location 103 and extends upward (towards the first arm shock pivot 42) such that the line 106 intersects the first arm wall 104 at the widest location of the hollow inner portion 86 between the narrow intermediate location 103 and the steering shaft 34 on the aft side.

The angle A′ for the outward taper of the lower end of the hollow inner portion 86 is defined in the forward direction when viewed in cross-section (FIGS. 4A-4W), by a third line 107 that begins on the forward side at the narrow intermediate location 103 and extends downward (towards the first arm fixed pivot 40) such that the line 107 intersects the first arm wall 104 at the widest location of the hollow inner portion 86, below the narrow intermediate location 103, of the first arm wall 104. The angle A for the outward taper of the lower end the hollow inner portion 86 is defined in the aft direction when viewed in cross-section (FIGS. 4A-4W), by a line 108 that begins on the aft side at the narrow intermediate location 103 and extends downward (towards the first arm fixed pivot 40) such that the line 108 intersects the first arm wall 104 at the widest location of the hollow inner portion 86, below the narrow intermediate location 103, of the first arm wall 104.

The disclosed wheel suspension assemblies can be designed to be lighter in weight, lower in friction, more compliant, safer, and perform better than traditional wheel suspension assemblies.

The disclosed wheel assemblies also reduce stiction and increase stability during braking, cornering, and shock absorption, when compared to traditional wheel suspension assemblies.

The disclosed wheel suspension assemblies are particularly well suited to E-bikes. E-bikes are heavier and faster than typical mountain bikes. They are usually piloted by less skilled and less fit riders, and require a stronger front suspension to handle normal riding conditions. E-bikes are difficult to build, requiring the challenging integration of motors and batteries into frame designs. In many cases, the electric parts are large and unsightly.

E-bikes are typically cost prohibitive to build as well, requiring special fittings to adapt motors and batteries. To integrate one center-drive motor, the additional cost to the manufacturer is about double the price of a common bicycle frame. That cost is multiplied and passed onto the consumer.

The beneficial caster effect described above with respect to the disclosed wheel suspension assemblies is an important improvement over traditional wheel suspension assemblies and reduces some of the drawbacks of E-bikes.

Additionally, because the disclosed wheel suspension assemblies are not constrained by round stantions, the oval fork legs balance fore-aft and side to side compliance for ultimate traction. Combining superior chassis stiffness while eliminating stiction gives the disclosed wheel suspension assemblies a performance advantage over traditional wheel suspension assemblies.

While a two-wheeled bicycle is disclosed, the disclosed wheel assemblies are equally applicable to any cycle, such as motorcycle, unicycle, or tricycle vehicles. Furthermore, the disclosed wheel suspension assemblies are easily retrofittable to traditional cycles.

Claims

1. A suspension assembly for a cycle, the suspension assembly comprising:

a fork having a first arm including a wall defining a hollow internal portion;

a plurality of interconnected links operatively connected to the first arm; and

a shock absorber at least partially disposed in the hollow internal portion,

wherein the hollow internal portion has a first end and a second end that are both wider than a narrow intermediate portion and the plurality of interconnected links comprises a wheel carrier having a wheel mount that is offset from a steering axis.

2. The suspension assembly of claim 1, wherein the hollow internal portion has a substantially hourglass shape when viewed in cross-section.

3. The suspension assembly of claim 2, wherein the first end and the second end are each wider than the narrow intermediate portion in the forward and aft direction.

4. The suspension assembly of claim 1, wherein the first end is wider than the second end.

5. The suspension assembly of claim 1, wherein the second end is wider than the first end.

6. (canceled)

7. (canceled)

8. The suspension assembly of claim 1, wherein the wheel mount is offset from the steering axis towards the first arm.

9. (canceled)

10. (canceled)

11. A suspension assembly for a cycle, the suspension assembly comprising:

a fork connected to a steering shaft having a steering axis, the fork including a first arm, and a second arm, the first arm having a wall defining a hollow internal portion, the hollow internal portion having a first end and a second end that are both wider than a narrow intermediate portion, the first arm also including a first arm fixed pivot, a first arm shock pivot, and a first arm control pivot;

a shock link, the shock link having a first shock link pivot and a second shock link pivot spaced apart from one another, the shock link being pivotably connected to the first arm fixed pivot at the first shock link pivot such that the shock link is rotatable about the first shock link pivot;

a shock absorber having a first shock mount and a second shock mount, the first shock mount being connected to the first arm shock pivot, the second shock mount being pivotably connected to a shock connection pivot located along a length of the shock link;

a wheel carrier, the wheel carrier having a wheel carrier first pivot and a wheel carrier second pivot spaced apart from one another along a length of the wheel carrier, and a wheel mount that is adapted to be connected to a wheel, the wheel carrier first pivot being pivotably connected to the second shock link pivot so that the wheel carrier second pivot is rotatable about the wheel carrier first pivot relative to the second shock link pivot; and

a control link, the control link including a control link floating pivot and a control link fixed pivot, the control link floating pivot being pivotably connected to the wheel carrier second pivot, and the control link fixed pivot being pivotably connected to the first arm control pivot such that the control link floating pivot is rotatable about the control link fixed pivot, which remains in a fixed location relative to the first arm control pivot,

wherein the wheel mount is offset from the steering axis.

12. The suspension assembly of claim 11, wherein the hollow internal portion is substantially hourglass-shaped when viewed in cross-section.

13. The suspension assembly of claim 12, wherein the first end and the second end are wider than the narrow intermediate portion in the forward and aft direction.

14. The suspension assembly of claim 11, wherein the first end is wider than the second end.

15. The suspension assembly of claim 11, wherein the second end is wider than the first end.

16. (canceled)

17. The suspension assembly of claim 11, wherein the wheel mount is offset from the steering axis towards the first arm.