FORM – 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
(See section 10 and rule 13)
A REINFORCED BELL-CRANK SUSPENSION SYSTEM WITH ANTI-BUCKLING
BALANCER ROD FOR INCREASED AXLE LOAD FOR VEHICLES
Applicant(s):
VE COMMERCIAL VEHICLES LTD
102, INDUSTRIAL AREA 1, PITHAMPUR- 454775, DIST. DHAR, MP, INDIA
Inventors:
(1) Sanket Prakash Kadale
(2) Raj Verma
The following specification particularly describes the invention and the manner in which it
is to be performed.
2
A REINFORCED BELL-CRANK SUSPENSION SYSTEM WITH
ANTI-BUCKLING BALANCER ROD FOR INCREASED AXLE LOAD
FOR VEHICLES
FIELD OF THE DISCLOSURE
[0001] this invention generally relates to a field of vehicle suspension systems, and5
in particular, to a reinforced bell-crank suspension system with anti-buckling
balancer rod for increased axle load for vehicles and method thereof.
BACKGROUND
[0002] The subject matter discussed in the background section should not be
assumed to be prior art merely as a result of its mention in the background section.10
Similarly, a problem mentioned in the background section or associated with the
subject matter of the background section should not be assumed to have been
previously recognized in the prior art. The subject matter in the background section
merely represents different approaches, which in and of themselves may also
correspond to implementations of the claimed technology.15
[0003] Bell-crank suspension systems are widely employed in heavy commercial
vehicles to support rear axle assemblies while providing ride stability, load
distribution, and controlled articulation of the chassis under varying road and
payload conditions. In conventional configurations, rear leaf springs, such as the R1
and R2 leaf spring assemblies, are typically positioned at a center-to-center distance20
of approximately 1.430 m. This arrangement has been widely adopted due to its
proven reliability, mechanical simplicity, and suitability for historical vehicle load
and operational requirements.
[0004] In such conventional rear suspension systems, the bell-crank assembly is
pivotably mounted to the chassis and cooperates with the rear leaf springs through25
a balance rod assembly. The leaf spring ends are supported by front and rear hanger
brackets and are interconnected with the chassis via shackles, pins, and U-bolts.
Wear plates are commonly employed at pivot interfaces to reduce friction and
extend service life. Proper alignment and articulation of these components are
critical for transmitting vertical loads from the chassis to the rear axle assembly,30
3
controlling deflection of the leaf springs, and maintaining ride stability during
braking, acceleration, cornering, and uneven road inputs.
[0005] However, with increasing regulatory and market demands for higher axle
loads and greater payload efficiency, the conventional 1.430 m leaf spring spacing
has become a limiting factor in effective load distribution. Under higher payload5
conditions, the shorter longitudinal spacing between R1 and R2 leaf springs results
in relatively higher bending moments on chassis side members and concentrated
load transfer through the spring hangers, bell-crank pivots, and balance rod
assembly. The compact spacing also limits the effective longitudinal spread of
forces along the rear axle assembly, which can cause uneven axle loading, reduce10
fatigue life of suspension components, and negatively impact vehicle handling and
stability during dynamic operating conditions.
[0006] The limited longitudinal spacing further affects load sharing between axles
during dynamic events, such as sudden braking, acceleration, cornering, and
traversing uneven surfaces. Under such conditions, the bell-crank assembly may15
experience increased pivoting forces, the leaf springs may undergo non-uniform
deflection, and the balance rod may be subjected to higher torsional stresses. These
factors collectively reduce the efficiency of load transfer, potentially resulting in
chassis stress concentrations, accelerated wear of pivot interfaces, and diminished
ride comfort and stability for the vehicle.20
[0007] Conventional approaches to address increased payload requirements often
involve the use of heavier leaf springs, reinforced chassis members, air suspension
systems, or complex hydraulic mechanisms to achieve higher axle load capability.
While such solutions can improve load distribution, they generally increase vehicle
cost, component mass, system complexity, and maintenance requirements.25
Additionally, these approaches may necessitate substantial redesign of existing
suspension architectures, which can complicate integration into established vehicle
platforms.
[0008] Accordingly, there exists a need for a mechanically efficient rear suspension
system that enhances load distribution, reduces stress concentrations, and increases30
axle load capability, while retaining the conventional bell-crank and leaf-spring
4
architecture. A solution that optimizes the geometry of the bell-crank lever,
increases the center-to-center spacing between R1 and R2 leaf springs, and
coordinates the operation of the balance rod, hanger brackets, shackles, and
fastening elements would enable higher payloads, improved ride stability, and
increased durability of suspension components without introducing significant5
complexity or cost to the vehicle.
[0009] Another the patent application, “US3369824A,” titled “Bell-crank spring-
suspension system for wheeled vehicles,” describes a suspension system for land
vehicles having a chassis provided with a pair of opposed sides and groundengaging
means, said chassis being normally positioned substantially parallel to a horizontal10
ground plane and said ground-engaging means being disposed, respectively, on
opposite sides of said chassis, said suspension system including means extending
and connected between said chassis at each side thereof and said ground-engaging
means, said last-named means comprising a pair of elongated members for each side
of said chassis, each of said members having a pair of supposed ends, means15
connecting one end of said of said members with, respectively, one of said ground-
engaging means, the other ends of said members converging toward one another
and being pivotally connected on the immediately-adjacent side of said chassis, an
inclined lever for each of said members, each of said levers having an end thereof
fixedly connected to its associated member with the other ends of said levers at each20
side of said chassis extending toward one another and into proximity with respect
to one another by linkage means, and substantially vertically disposed resilient
means pivotally connected at one end with each pair of said proximate ends through
said linkage means and being pivotally connected at the other end to the adjacent
side of said chassis for swinging movement about a horizontal pivot axis, said25
resilient means constantly biasing said one end of said members for swinging
movement in contra directions.
[0010] Another patent application, "US8864153B2," titled "Automotive rear
suspension subassembly," describes an automotive rear-suspension subassembly
includes a rear-suspension frame, a first and second independent suspension, and a30
steering actuator coupled with each independent suspension through a bellcrank.
5
The frame includes a front cross-member, a first side-rail, and a second side-rail,
and defines a first side and a second side. The actuator is disposed on the first side
of the frame, and the bellcrank extends across the frame from the first side to the
second side. Each independent suspension is respectively configured to support a
vehicle wheel, and includes a respective knuckle. Actuation of the steering actuator5
urges each respective knuckle to rotate.
[0011] In conventional heavy commercial vehicle rear suspension arrangements,
effective load distribution and axle support are largely dependent on the relative
positioning of leaf springs, bell-crank assemblies, balance rods, and associated
fastening elements. Such arrangements typically rely on a compact center-to-center10
spacing of rear leaf springs, along with discrete hanger brackets, shackles, pins, U-
bolts, and wear plates to transmit vertical loads from the chassis to the rear axle
assembly. As a result, installation and maintenance of conventional rear suspension
systems often require precise alignment of multiple suspension components, careful
coordination of pivot interfaces, and accommodation of limited longitudinal spacing15
between spring assemblies. These requirements make conventional suspension
solutions less adaptable to vehicles designed for higher payloads or more demanding
operating conditions, particularly where increased axle load, dynamic load sharing,
and stress distribution are critical. While traditional bell-crank and leaf-spring
architectures can provide reliable ride support under standard loads, they introduce20
concentrated stress points, potential fatigue at pivot interfaces, and limitations on
payload capacity, thereby constraining durability, stability, and scalability for
modern heavy-duty vehicle platforms.
OBJECTIVES OF THE INVENTION
[0012] The objective of the present invention is to provide a reinforced bell-crank25
suspension system with anti-buckling balancer rod for increased axle load for
vehicles, incorporating an increased center-to-center distance of approximately
1.8 m between rear leaf spring assemblies, configured to redistribute loads across
the rear axle assembly and increase axle load capacity without requiring
reinforcement of chassis, springs, or other structural components.30
6
[0013] The objective of the present invention is to overcome limitations of
conventional compact leaf-spring spacing by geometrically optimizing the bell-
crank lever and rear leaf spring arrangement, thereby reducing stress concentrations
on the chassis, spring hangers, and bell-crank pivots while maintaining ride stability
and suspension articulation under high payload conditions.5
[0014] The objective of the present invention is to achieve higher axle loads and
improved load-sharing between axles through a purely passive mechanical
suspension system, without reliance on additional air suspension, hydraulic
mechanisms, or electronic control systems.
[0015] The objective of the present invention is to provide a scalable and retrofit-10
friendly rear suspension configuration that can be integrated into existing heavy
commercial vehicle platforms with minimal modification, assembly effort, or
disruption to established chassis architecture.
[0016] The objective of the present invention is to optimize rear axle geometry and
component positioning to leverage regulatory and design load thresholds, thereby15
enhancing functional performance, durability, and compliance under real-world
operating conditions.
[0017] The objective of the present invention is to maintain controlled deflection
and articulation of The pair of rear leaf spring assemblies, bell-crank assembly, and
balance rod, ensuring uniform load transfer, reduced dynamic stresses, and20
improved ride comfort across varying road surfaces and payload conditions.
[0018] The objective of the present invention is to reduce concentrated bending
moments and localized fatigue on suspension components, enabling longer service
life and reliable performance under repeated high-load and dynamic operating
cycles.25
[0019] The objective of the present invention is to provide a mechanically simple,
robust, and cost-effective suspension solution that enhances payload capacity and
vehicle stability while preserving the proven reliability and durability of
conventional bell-crank and leaf-spring architectures.
SUMMARY30
7
[0020] The present invention relates to a reinforced bell-crank suspension system
with anti-buckling balancer rod for increased axle load for vehicles.
[0021] According to an aspect, a reinforced bell-crank suspension system with
anti-buckling balancer rod for increased axle load for vehicles is disclosed. The
reinforced bell-crank suspension system comprises a rear axle assembly operatively5
associated with a chassis of the vehicle. The reinforced bell-crank suspension
system further comprises a pair of rear leaf spring assemblies positioned on opposite
sides of the rear axle assembly. The reinforced bell-crank suspension system further
comprises a bell-crank assembly including at least one bell crank pivotably mounted
to the chassis and operatively coupled to the pair of rear leaf spring assemblies10
through a balance rod assembly. The reinforced bell-crank suspension system with
anti-buckling balancer rod for increased axle load for vehicles further comprises a
front hanger bracket and a rear hanger bracket configured to support respective ends
of each rear leaf spring assembly. The reinforced bell-crank suspension system
further comprises a shackle connecting at least one end of each rear leaf spring15
assembly to the chassis. The reinforced bell-crank suspension system further
comprises a plurality of fastening elements including pins, U-bolts, and wear plates
configured to secure and articulate the suspension components. Further, a centre-to-
centre distance between the pair of rear leaf spring assemblies is increased to
approximately 1.8 meters. Further, the bell-crank lever geometry is configured to20
preserve an original suspension motion ratio despite the increased centre-to-centre
distance. Further, cooperative engagement of the pair of rear leaf spring assemblies,
the bell-crank assembly, and the balance rod assembly redistributes vertical loads
more uniformly across the rear axle assembly, thereby increasing axle load
capability while maintaining ride stability and durability without the use of auxiliary25
air or hydraulic systems.
[0022] According to another aspect, a method for providing a reinforced bell-crank
suspension system with anti-buckling balancer rod for increased axle load for
vehicles is disclosed. The method comprises steps of providing a rear axle assembly
operatively associated with a chassis of the vehicle. The method further comprises30
steps of positioning a pair of rear leaf spring assemblies on opposite sides of the rear
8
axle assembly. The method further comprises steps of mounting a bell-crank
assembly including at least one bell crank pivotably to the chassis and operatively
coupling to the pair of rear leaf spring assemblies through a balance rod assembly.
The method further comprises steps of supporting a front hanger bracket and a rear
hanger bracket respective ends of each rear leaf spring assembly. The method5
further comprises steps of connecting, via a shackle, at least one end of each rear
leaf spring assembly to the chassis. The method further comprises steps of securing
and articulating, via a plurality of fastening elements including pins, U-bolts, and
wear plates, the suspension components. Further, a centre-to-centre distance
between the pair of rear leaf spring assemblies is increased to approximately 1.810
meters. Further, the bell-crank lever geometry is configured to preserve an original
suspension motion ratio despite the increased centre-to-centre distance. Further,
cooperative engagement of the pair of rear leaf spring assemblies, the bell-crank
assembly, and the balance rod assembly redistributes vertical loads more uniformly
across the rear axle assembly, thereby increasing axle load capability while15
maintaining ride stability and durability without the use of auxiliary air or hydraulic
systems.
BRIEF DESCRIPTION OF THE DRAWINGS
[0023] The accompanying drawings illustrate various embodiments of systems,
methods, and embodiments of various other aspects of the disclosure. Any person20
with ordinary skills in the art will appreciate that the illustrated element boundaries
(e.g., boxes, groups of boxes, or other shapes) in the figures represent one example
of the boundaries. It may be that in some examples one element may be designed as
multiple elements or that multiple elements may be designed as one element. In
some examples, an element shown as an internal component of one element may be25
implemented as an external component in another, and vice versa. Furthermore,
elements may not be drawn to scale. Non-limiting and non-exhaustive descriptions
are described with reference to the following drawings. The components in the
figures are not necessarily to scale, emphasis instead being placed upon illustrating
principles.30
9
[0024] FIG. 1 illustrates a perspective view of a reinforced bell-crank suspension
system with anti-buckling balancer rod for increased axle load for vehicles for a
vehicle, according to an embodiment of the present disclosure;
[0025] FIG. 2 illustrates an exploded view of the reinforced bell-crank suspension
system, according to an embodiment of the present disclosure; and5
[0026] FIG. 3 illustrates a flowchart showing a method for providing the reinforced
bell-crank suspension system with anti-buckling balancer rod for increased axle
load for vehicles, according to an embodiment of the present disclosure.
DETAILED DESCRIPTION
[0027] Some embodiments of this disclosure, illustrating all its features, will now10
be discussed in detail. The words “comprising,” “having,” “containing,” and
“including,” and other forms thereof, are intended to be equivalent in meaning and
be open ended in that an item or items following any one of these words is not meant
to be an exhaustive listing of such item or items or meant to be limited to only the
listed item or items. It must also be noted that as used herein and in the appended15
claims, the singular forms “a,” “an,” and “the” include plural references unless the
context clearly dictates otherwise.
[0028] Although any systems and methods similar or equivalent to those described
herein can be used in the practice or testing of embodiments of the present
disclosure, the preferred, systems and methods are now described. Embodiments of20
the present disclosure will be described more fully hereinafter with reference to the
accompanying drawings in which like numerals represent like elements throughout
the several figures, and in which example embodiments are shown. Embodiments
of the claims may, however, be embodied in many different forms and should not
be construed as limited to the embodiments set forth herein. The examples set forth25
herein are non-limiting examples and are merely examples among other possible
examples.
[0029] The present invention discloses various embodiments of a reinforced
bell-crank suspension system with anti-buckling balancer rod for increased axle
load for vehicles is disclosed. The reinforced bell-crank suspension system30
comprises a rear axle assembly operatively associated with a chassis of the vehicle.
10
The reinforced bell-crank suspension system further comprises a pair of rear leaf
spring assemblies positioned on opposite sides of the rear axle assembly. The
reinforced bell-crank suspension system further comprises a bell-crank assembly
including at least one bell crank pivotably mounted to the chassis and operatively
coupled to the pair of rear leaf spring assemblies through a balance rod assembly.5
The reinforced bell-crank suspension system further comprises a front hanger
bracket and a rear hanger bracket configured to support respective ends of each rear
leaf spring assembly. The reinforced bell-crank suspension system further
comprises a shackle connecting at least one end of each rear leaf spring assembly to
the chassis. The reinforced bell-crank suspension system further comprises a10
plurality of fastening elements including pins, U-bolts, and wear plates configured
to secure and articulate the suspension components. Further, a centre-to-centre
distance between the pair of rear leaf spring assemblies is increased to
approximately 1.8 meters. Further, the bell-crank lever geometry is configured to
preserve an original suspension motion ratio despite the increased centre-to-centre15
distance. Further, cooperative engagement of the pair of rear leaf spring assemblies,
the bell-crank assembly, and the balance rod assembly redistributes vertical loads
more uniformly across the rear axle assembly, thereby increasing axle load
capability while maintaining ride stability and durability without the use of auxiliary
air or hydraulic systems.20
[0030] FIG. 1 illustrates a perspective view of a reinforced bell-crank suspension
system (100) with anti-buckling balancer rod for increased axle load for vehicles,
according to an embodiment of the present disclosure. FIG. 2 illustrates an exploded
view of the reinforced bell-crank suspension system (100), according to an
embodiment of the present disclosure.25
[0031] The reinforced bell-crank suspension system (100) for a vehicle comprises
a rear axle assembly (102) operatively associated with a chassis (104) of the vehicle,
and a pair of rear leaf spring assemblies (106) positioned on opposite sides of the
rear axle assembly (102). The pair of rear leaf spring assemblies (106) are arranged
at an increased centre-to-centre distance of approximately 1.8 meters, thereby30
enabling improved longitudinal load distribution across the rear axle assembly
11
(102). The bell-crank assembly (108), including at least one bell crank pivotably
mounted to the chassis (104), is operatively coupled to the pair of rear leaf spring
assemblies (106) through a balance rod assembly. The rear suspension system also
comprises a front hanger bracket (110) and a rear hanger bracket configured to
support respective ends of each rear leaf spring assembly, a shackle (112)5
connecting at least one end of each rear leaf spring assembly to the chassis (104),
and a plurality of fastening elements (114) including pins, U-bolts, and wear plates
configured to secure and articulate the suspension components.
[0032] In one embodiment, the increased centre-to-centre distance between the pair
of rear leaf spring assemblies (106) redistributes vertical loads more uniformly10
across the rear axle assembly (102), thereby increasing axle load capability while
maintaining ride stability and durability without the use of auxiliary air or hydraulic
systems. The cooperative engagement of the pair of rear leaf spring assemblies
(106), bell-crank assembly (108), and balance rod assembly reduces localized stress
concentrations on the chassis (104), bell-crank pivots, and hanger brackets during15
vehicle operation. The optimized spacing allows the rear axle assembly (102) to
function as an effectively longer load-sharing axle group, which enhances payload
capacity and improves overall suspension performance under high-load conditions.
[0033] In another embodiment, the bell-crank assembly (108) includes a wear plate
positioned at the pivot interface to reduce frictional wear and extend service life20
under increased axle loads. The wear plate ensures smooth pivoting of the bell crank
and prevents premature fatigue at critical articulation points. The design maintains
the original suspension motion ratio despite the increased centre-to-centre spacing,
enabling the bell-crank assembly (108) to preserve ride comfort and maintain
suspension articulation characteristics equivalent to a suspension system with a25
smaller longitudinal spacing of the leaf springs.
[0034] The balance rod assembly is configured to synchronize deflection of the pair
of rear leaf spring assemblies (106) to promote balanced load sharing across the rear
axle assembly (102). In some embodiments, the balance rod assembly compensates
for uneven loading and dynamic road inputs, maintaining uniform suspension30
response across the left and right sides of the vehicle. By coordinating movement
12
between the rear leaf springs and the bell-crank assembly (108), the balance rod
ensures smooth transfer of forces and reduces the likelihood of excessive stress
concentrations on the chassis (104) and pivot points.
[0035] The front hanger bracket (110) and the rear hanger bracket are positioned to
accommodate the increased longitudinal spacing of the pair of rear leaf spring5
assemblies (106) without modification to the fundamental leaf-spring architecture.
The shackle (112) permits controlled articulation of each rear leaf spring assembly
relative to the chassis (104), enabling compliance under dynamic loading and
uneven road surfaces. In combination, the hanger brackets and shackle (112)s allow
the suspension system to maintain consistent leaf spring alignment and proper load10
transfer while preserving the inherent durability and reliability of conventional
suspension designs.
[0036] The plurality of fastening elements (114), including pins and U-bolts, are
configured to withstand increased axle loads without requiring an increase in
material thickness or component mass. The arrangement of fastening elements15
secures the bell-crank assembly (108), leaf springs, and hanger brackets while
allowing pivoting motion and articulation as required. The design of the fastening
elements ensures robust mechanical engagement under dynamic operating
conditions, prevents loosening under repeated loads, and contributes to the overall
structural integrity of the rear suspension system.20
[0037] In operation, the reinforced bell-crank suspension system (100) effectively
redistributes loads across the rear axle assembly (102), enabling higher payload
capacity and improved ride stability without reliance on auxiliary systems. The
optimized bell-crank geometry, extended leaf spring spacing, balance rod
coordination, and wear-reducing elements collectively provide a mechanically25
simple, robust, and durable solution. The system is scalable and retrofit-friendly,
allowing integration into existing vehicle platforms with minimal modification,
while preserving the proven reliability and performance characteristics of
conventional bell-crank and leaf-spring architectures.
13
[0038] FIG. 3 illustrates a flowchart showing a method (300) for providing the
reinforced bell-crank suspension system (100) for a vehicle, according to an
embodiment of the present disclosure.
[0039] At operation 302, the rear axle assembly (102) is provided and operatively
associated with the chassis (104) of the vehicle.5
[0040] At operation 304, the pair of rear leaf spring assemblies (106) are positioned
on opposite sides of the rear axle assembly (102). The pair of rear leaf spring
assemblies (106) are arranged at an increased centre-to-centre distance of
approximately 1.8 meters, thereby enabling improved longitudinal load distribution
across the rear axle assembly (102).10
[0041] At operation 306, the bell-crank assembly (108) including at least one bell
crank pivotably is mounted to the chassis (104) and is operatively coupled to the
pair of rear leaf spring assemblies (106) through a balance rod assembly.
[0042] At operation 308, the front hanger bracket (110) and the rear hanger bracket
configured to support respective ends of each rear leaf spring assembly. The front15
hanger bracket (110) and the rear hanger bracket are positioned to accommodate the
increased longitudinal spacing of the pair of rear leaf spring assemblies (106)
without modification to the fundamental leaf-spring architecture.
[0043] At operation 310, the shackle (112) connecting the at least one end of each
rear leaf spring assembly to the chassis (104). The shackle (112) permits controlled20
articulation of each rear leaf spring assembly relative to the chassis (104), enabling
compliance under dynamic loading and uneven road surfaces. In combination, the
hanger brackets and shackle (112) allow the suspension system to maintain
consistent leaf spring alignment and proper load transfer while preserving the
inherent durability and reliability of conventional suspension designs.25
[0044] At operation 312, the plurality of fastening elements (114) including pins,
U-bolts, and wear plates are configured to secure and articulate the suspension
components. Further, the centre-to-centre distance between the pair of rear leaf
spring assemblies (106) is increased to approximately 1.8 meters. Further, the bell-
crank lever geometry is configured to preserve an original suspension motion ratio30
despite the increased centre-to-centre distance. Further, cooperative engagement of
14
the pair of rear leaf spring assemblies (106), the bell-crank assembly (108), and the
balance rod assembly redistributes vertical loads more uniformly across the rear axle
assembly (102), thereby increasing axle load capability while maintaining ride
stability and durability without the use of auxiliary air or hydraulic systems.
[0045] In operation, the reinforced bell-crank suspension system (100) effectively5
redistributes loads across the rear axle assembly (102), enabling higher payload
capacity and improved ride stability without reliance on auxiliary systems. The
optimized bell-crank geometry, extended leaf spring spacing, balance rod
coordination, and wear-reducing elements collectively provide a mechanically
simple, robust, and durable solution. The system is scalable and retrofit-friendly,10
allowing integration into existing vehicle platforms with minimal modification,
while preserving the proven reliability and performance characteristics of
conventional bell-crank and leaf-spring architectures.
[0046] Various embodiments of the present invention provide notable advantages
through a reinforced bell-crank suspension system (100) comprising a rear axle15
assembly (102), a pair of rear leaf spring assemblies (106), a bell-crank assembly
(108), a balance rod assembly, hanger brackets, shackle (112)s, and fastening
elements configured for cooperative engagement. The increased centre-to-centre
spacing between R1 and R2 leaf springs improves load distribution along the rear
axle assembly (102), reducing peak bending moments on the chassis (104) and20
enhancing structural durability. The suspension system enables higher axle load
capacity, on the order of approximately one ton per axle, without necessitating over-
design of the leaf springs, bell-crank assembly (108), or other structural
components, thereby meeting updated regulatory axle load norms. By reducing
cyclic stresses on the leaf springs, bell-crank pivots, and associated fastening25
elements, the suspension extends fatigue life and overall service life of the rear
suspension system. The optimized geometry and longer axle spacing improve ride
stability and articulation over uneven terrain, mitigating pitch and hop during
braking, acceleration, and dynamic loading events. More uniform load transfer
further reduces dynamic axle load variation, minimizes tyre wear, and decreases30
15
road surface damage, while maintaining mechanical simplicity, durability, and
reliable operational performance across diverse vehicle applications.
[0047] It has thus been seen the reinforced bell-crank suspension system (100) with
anti-buckling balancer rod for increased axle load for vehicles, as described. The
reinforced bell-crank suspension system (100) in any case could undergo numerous5
modifications and variants, all of which are covered by the same innovative concept;
moreover, all of the details can be replaced by technically equivalent elements. In
practice, the components used, as well as the numbers, shapes, and sizes of the
components can be whatever according to the technical requirements. The scope of
protection of the invention is therefore defined by the attached claims.10

CLAIMS

1. A reinforced bell-crank suspension system (100) with anti-buckling balancer
rod for increased axle load for vehicles, the reinforced bell-crank suspension
system (100) comprising:5
a rear axle assembly (102) operatively associated with a chassis (104)
of a vehicle;
a pair of rear leaf spring assemblies (106) positioned on opposite sides
of the rear axle assembly (102);
a bell-crank assembly (108) including at least one bell crank pivotably10
mounted to the chassis (104) and operatively coupled to the pair of rear leaf
spring assemblies (106) through a balance rod assembly;
a front hanger bracket (110) and a rear hanger bracket configured to
support respective ends of each rear leaf spring assembly;
a shackle (112) connecting at least one end of each rear leaf spring15
assembly to the chassis (104); and
a plurality of fastening elements (114) including pins, U-bolts, and
wear plates configured to secure and articulate the suspension components,
wherein a centre-to-centre distance between the pair of rear leaf spring
assemblies (106) is increased to approximately 1.8 meters,20
wherein the bell-crank lever geometry is configured to preserve an
original suspension motion ratio despite the increased centre-to-centre
distance, and
wherein cooperative engagement of the pair of rear leaf spring
assemblies (106), the bell-crank assembly (108), and the balance rod25
assembly redistributes vertical loads more uniformly across the rear axle
assembly (102), thereby increasing axle load capability while maintaining
ride stability and durability without the use of auxiliary air or hydraulic
systems.
2. The reinforced bell-crank suspension system (100) as claimed in claim 1,
wherein the increased centre-to-centre distance between the pair of rear leaf
spring assemblies (106) reduces localized stress concentrations on the chassis
(104), bell-crank pivots, and hanger brackets during vehicle operation.
3. The reinforced bell-crank suspension system (100) as claimed in claim 1,5
wherein the bell-crank assembly (108) includes a wear plate positioned at a
pivot interface to reduce frictional wear and extend service life under
increased load conditions.
4. The reinforced bell-crank suspension system (100) as claimed in claim 1,
wherein the balance rod assembly is configured to synchronize deflection of10
the pair of rear leaf spring assemblies (106) to promote balanced load sharing
across the rear axle assembly (102).
5. The reinforced bell-crank suspension system (100) as claimed in claim 1,
wherein the front hanger bracket (110) and the rear hanger bracket are
positioned to accommodate the increased longitudinal spacing of the pair of15
rear leaf spring assemblies (106) without modification to a fundamental leaf-
spring architecture.
6. The reinforced bell-crank suspension system (100) as claimed in claim 1,
wherein the shackle (112) permits controlled articulation of the pair of rear
leaf spring assemblies (106) to maintain suspension compliance under20
dynamic loading and uneven road conditions.
7. The reinforced bell-crank suspension system (100) as claimed in claim 1,
wherein the bell-crank lever geometry is optimized to maintain ride comfort
and suspension articulation characteristics equivalent to those of a suspension
having a smaller centre-to-centre spring distance.25
8. The reinforced bell-crank suspension system (100) as claimed in claim 1,
wherein the fastening elements including the pins and U-bolts are configured
to withstand increased axle loads without requiring an increase in material
thickness or component mass.
9. The reinforced bell-crank suspension system (100) as claimed in claim 1,30
wherein the increased centre-to-centre distance causes the rear axle assembly
(102) to function as an effectively longer load-sharing axle group, enabling
higher payload capacity while preserving mechanical simplicity and
reliability.
10. A method (300) for providing a reinforced bell-crank suspension system
(100) with anti-buckling balancer rod for increased axle load for vehicles, the5
method (300) comprising:
providing a rear axle assembly (102) operatively associated with a
chassis (104) of a vehicle;
positioning a pair of rear leaf spring assemblies (106) on opposite
sides of the rear axle assembly (102);10
mounting a bell-crank assembly (108) including at least one bell crank
pivotably to the chassis (104) and operatively coupling to the pair of rear leaf
spring assemblies (106) through a balance rod assembly;
supporting a front hanger bracket (110) and a rear hanger bracket
respective ends of each rear leaf spring assembly;15
connecting, via a shackle (112), at least one end of each rear leaf
spring assembly to the chassis (104); and
securing and articulating, via a plurality of fastening elements (114)
including pins, U-bolts, and wear plates, the suspension components,
wherein a centre-to-centre distance between the pair of rear leaf spring20
assemblies (106) is increased to approximately 1.8 meters,
wherein the bell-crank lever geometry is configured to preserve an
original suspension motion ratio despite the increased centre-to-centre
distance, and
wherein cooperative engagement of the pair of rear leaf spring25
assemblies (106), the bell-crank assembly (108), and the balance rod
assembly redistributes vertical loads more uniformly across the rear axle
assembly (102), thereby increasing axle load capability while maintaining
ride stability and durability without the use of auxiliary air or hydraulic
systems.