U.S. patent number 3,731,913 [Application Number 05/131,148] was granted by the patent office on 1973-05-08 for springs.
This patent grant is currently assigned to Dunlop Holdings Limited. Invention is credited to Archie J. Hirst, deceased.
United States Patent |
3,731,913 |
Hirst, deceased |
May 8, 1973 |
SPRINGS
Abstract
A spring and a suspension system primarily for railway vehicles,
comprising a chevron-type rubber sandwich spring in which the
spring width increases towards the apex end of the spring wherein
the central region of the apex-end of the spring is cored-out to
provide a cavity extending into the spring. Of which the following
is a specification.
Inventors: |
Hirst, deceased; Archie J.
(late of Leicester, EN) |
Assignee: |
Dunlop Holdings Limited
(London, EN)
|
Family
ID: |
10074550 |
Appl.
No.: |
05/131,148 |
Filed: |
April 5, 1971 |
Foreign Application Priority Data
|
|
|
|
|
Apr 7, 1970 [GB] |
|
|
16,284/70 |
|
Current U.S.
Class: |
267/294 |
Current CPC
Class: |
F16F
1/41 (20130101); F16F 1/40 (20130101); B61F
5/305 (20130101) |
Current International
Class: |
B61F
5/30 (20060101); B61F 5/00 (20060101); F16F
1/41 (20060101); F16F 1/40 (20060101); F16F
1/36 (20060101); F16f 001/36 () |
Field of
Search: |
;267/63 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Marbert; James B.
Claims
Having now described my invention what I claim is:
1. A chevron-type spring for use under compressive and shear
loading comprising a stack of V-shaped cross-section resilient
blocks having parallel V-shaped cross-section metal plates
interleaved between and bonded to the resilient blocks, the stack
terminating in end plates, the end plate, blocks and interleaves at
the apex end of the spring being wider than the end plate, blocks
and interleaves at the other end of the spring, the central region
of the wider end of the spring being cored-out to provide a cavity
extending through the associated end plate and into at least the
resilient block adjacent the said associated end plate whereby the
bending stress on at least the first intermediate plate from the
wider end of the spring is reduced.
2. A spring as in claim 1 wherein the cavity extends through the
whole stack of V-shaped resilient blocks and plates.
3. A spring as in claim 1 wherein the cavity has a progressively
reducing cross-sectional area in a direction into the stack from
the apex end of the spring.
4. A spring as in claim 1 wherein the plates and blocks are of
reducing length towards the apex end of the spring, the length
being the dimension of the plate or block along the apex of the
V-shape.
5. A spring as in claim 1 wherein at least the two blocks at the
apex end of the spring are equal in length.
6. A spring as in claim 1 wherein successive resilient blocks are
displaced in a common direction perpendicular to the direction of
stacking of the blocks so that the stack has an echelon
profile.
7. A vehicle axle suspension device comprising two springs
according to claim 1 one end of each spring being operatively
associated with an axle box housing and the other end of the spring
being arranged to be operatively associated with a sprung portion
of the vehicle, the operative association with the housing being
such that when mounted in the operational position in the
associated vehicle the springs are arranged in spaced apart
relationship considered longitudinally relative to the vehicle.
8. A vehicle axle suspension device as in claim 7 wherein the apex
end of the spring is operatively associated with an abutment
provided on the axle box housing.
9. A vehicle axle suspension as in claim 7 wherein the apex end of
the spring is operatively associated with an abutment provided on
the sprung portion of the vehicle.
10. A vehicle axle suspension as in claim 7 wherein the cored-out
portion of the spring is closed by the associated abutment member
to prevent the ingress of contaminants.
11. A vehicle axle suspension system comprising an axle assembly
suspended at each end from an associated vehicle frame by an axle
suspension as in claim 7.
Description
This invention relates to chevron type springs for use under
compressive and shear loading, of the type comprising a stack of
resilient blocks having parallel metal plates interleaved between
and bonded to the resilient blocks, the blocks and plates each
being of V-shaped cross-section, that is, taking the form of a
V-shaped trough, and to vehicle suspension units and systems
incorporating springs of the type described.
When a spring of the type described above is subjected to
compressive and shear loading the spring is deflected to a position
in which the internal stresses in the spring are in a state of
equilibrium with the external forces. Under this loading the plates
and blocks tend to open out imposing high bending stresses on the
intermediate plates. In such springs it is essential to ensure that
the range of bending stresses imposed at the apices of the metal
plates during use of the spring does not exceed the fatigue limit
of the metal with regard to the required spring life in cycles.
The intermediate plates also tend to cant relative to the outer
plates and the associated resilient blocks become deformed to wedge
shapes. This deformation gives an uneven distribution of stress in
the blocks which may place an excessive stress on some parts of the
spring resulting in a reduction in the life of the spring and
placing a limitation on the load-carrying capacity of the
spring.
Reduction of the bending moment on the intermediate metal plates of
springs of the type described above by progressively increasing the
width of the plates and blocks from one end of the spring to the
other is already known and disclosed in British Patent
specification No. 720,365.
Reduction of the tendency of the plates to cant by progressively
displacing and decreasing the length of the resilient blocks and
plates in a direction at right angles to their direction of
stacking is also already known and disclosed in British Patent
specification No. 753,995.
One object of the present invention is to provide an improved
spring of the type described above.
According to one aspect of the present invention a chevron-type
spring for use under compressive and shear loading comprises a
stack of V-shaped cross-section resilient blocks having parallel
V-shaped cross-section metal plates interleaved between and bonded
to the resilient blocks, the stack terminating in end plates, the
end plate, blocks and interleaves at the apex end of the spring
being wider than the end plate, blocks and interleaves at the other
end of the spring, the central region of the wider end of the
spring being cored-out to provide a cavity extending through the
associated end plate and into at least the resilient block adjacent
the said associated end plate.
Successive resilient blocks of the spring described in the
preceding paragraph may be progressively displaced in a common
direction perpendicular to the direction of stacking of the blocks
so that the spring has an echelon profile.
According to another aspect of the present invention a vehicle axle
suspension device comprises two springs as described in either of
the preceding paragraphs, one end of each spring being operatively
associated with an axle box housing and the other end of the spring
being arranged to be operatively associated with a sprung portion
of the associated vehicle, the operative association of the springs
with the housing being such that when mounted in an operational
position on the associated vehicle the springs are arranged in
spaced-apart relationship considered longitudinally relative to the
vehicle.
According to a further aspect of the present invention a vehicle
axle suspension system comprises an axle assembly suspended at each
end from an associated vehicle body structure by two devices as
described in the preceding paragraph.
Some embodiments of the invention will now be described by way of
example only, in conjunction with the accompanying diagrammatic
drawing in which:
FIG. 1 is a part-sectional side view of a suspension for an
axlebox.
FIG. 2 is a part-sectional top view of the suspension in FIG. 1 on
the line II--II of FIG. 1.
FIG. 3 is a part section on the line III--III of FIG. 2.
FIG. 4 is a part section of the spring unit of FIG. 1.
FIG. 5 is an alternative spring unit.
FIG. 6 is a section on line VI--VI of FIG. 5.
FIGS. 7 and 8 show diagrammatically springs used for explanation of
the principles involved.
In FIG. 1 an axle suspension assembly for a rail vehicle comprises
two chevron type spring units 1, 2. Each spring unit comprises a
stack of five V-shaped cross-section rubber blocks 3 with parallel
V-shaped cross-section steel plates 4 interleaved between and
bonded to the rubber blocks 3, both ends of the stack terminating
in steel end plates 5 and 6. Successive spring blocks 3 are
progressively displaced in a common direction perpendicular to the
direction of stacking of the blocks 3 so that the spring units 1, 2
have an echelon profile when viewed in a plane containing the
directions of stacking and displacement of the rubber blocks 3.
The spring units 1, 2 are connected to an associated axlebox 7. The
axlebox 7 has bearings which support one end of the vehicle axle
unit 8. The springs 1, 2 are mounted in spaced relationship
considered longitudinally of the vehicle with the apex ends 5 of
the spring units 1, 2 attached to the axlebox 7 and the other ends
6 attached to the vehicle underframe 9, the ends 6 of the spring
units connected to the underframe 9 being higher and longitudinally
spaced further than the ends 5 associated with the axlebox 7 so
that the vehicle weight is supported by shear and compressive
forces in the spring units 1, 2.
The width of each spring unit 1, 2, that is the dimension of the
spring unit in a direction at right angles to the direction of
stacking and displacement of the spring unit, is arranged to
progressively decrease from the apex end 5 of the spring to the
other end 6 of the spring unit in the manner disclosed in the
specification of U.K. Pat. No. 720,365.
The wider (when viewed in plan) apex end 5 of each spring unit is
cored-out to provide a cavity 10 which extends through the end
plate 5 and the first two rubber blocks 3 and associated
interleaving plates 4 positioned nearest the apex end 5 of the
spring unit, terminating in the third block from the apex end 5 of
the spring unit.
The end plate attachment to the vehicle underframe 9 comprises an
adaptor block 11 which engages a vertically-extending cut-out 12
formed in the underframe 9. This arrangement provides transverse
location of the spring unit. Vertical location is achieved by means
of the adaptor block 11 abutting the adjacent underside of the
underframe 9.
The end plate 5 of each spring unit which is arranged to be
operatively associated with the axle is provided with studs 13 to
engage sockets 14 formed in the associated vehicle axle box 7. The
arrangement of the studs 13 and sockets 14 is such that provided
the end plate 5 is biased towards the axle box housing by the
associated spring vertical movement of the end plate 5 relative to
the axle box 7 is prevented. If required the axle box housing and
associated end plates may be permanently secured together. The
studs 13 may alternatively be provided with split-pins or other
similar releasable means to hold the springs in engagement with the
axle box housing. This simplifies the attachment of the suspension
device to the associated bogie.
The cavity 10 provided in the apex end 5 of the spring effectively
removes the apex of the chevron in the central region of the spring
and allows the chevron to be mounted closer to the center of the
axle thus reducing the overall longitudinal dimension of the
suspension unit. Also when the wider plates and blocks are mounted
immediately adjacent the axle it is possible to accommodate wider
blocks and plates by recessing the rear face of the adjacent wheel
(see FIG. 2).
The connection between the spring end plate 5 and the axlebox 7
prevents atmospheric and fluid contaminants from entering the
spring cavity 10.
In the spring constructions shown in FIGS. 1-4 of the accompanying
drawings the four plates and blocks nearest the apex end of the
spring are substantially equal in length and are slightly shorter
than the two plates and the intermediate block nearest the other
end of the spring. The increase in the length, as compared with a
normal chevron spring, of the four plates and blocks nearest the
apex end of the spring, achieved by using plates and blocks of
equal length as opposed to plates and blocks which decrease in
length, increases the stability of the spring against buckling
about an axis parallel to the associated axle.
The spring construction disclosed in FIGS. 5 and 6 of the
accompanying drawings employs plates in which the lengths of the
plates and blocks progressively decrease towards the apex end of
the spring. This is made possible as the percentage of the volume
of the spring which is cored-out is smaller than in the spring
arrangements shown in FIGS. 1-4 and thus the additional stability
achieved by using plates and blocks of equal length, as opposed to
progressively decreasing length, at the apex end of the spring is
no longer required, since the spring possesses increased stability
as a result of the proportionally smaller cavity.
When the suspension device is mounted in its operational position
the directions of stacking and displacement of the spring blocks
are arranged to lie in a vertical plane which is substantially
parallel with the longitudinal axis of the bogie as shown in FIG.
1.
The plane containing the directions of stacking and displacement of
the spring blocks can be inclined with respect to the longitudinal
axis of the bogie if design considerations so require.
Although in the axle suspension device and system described above
the apex end of the spring is operatively associated with the axle
box this situation may be reversed if design considerations
dictate.
An axle suspension system can be provided by supporting each end of
a vehicle axle by a suspension device as described above.
The benefits derived from coring-out the wider end of the chevron
will now be explained for simplicity with reference to a chevron
spring in which the blocks are not progressively displaced in a
direction at right angles to the direction of stacking of the
blocks. It should be understood, however, that the same explanation
also applies to echelon profile chevrons.
Consider the section through a constant width chevron shown in FIG.
7, taken in the plane containing the centers of pressure of the
blocks. The bending moment acting on each intermediate plate, for
example, plate A, about a point B on the center-line C of the
spring is as follows.
Considering the half of the spring above the center-line C of FIG.
7 each half block above this line C can be considered to have its
own center of pressure D. The distance X of the center of pressure
of the half block E from the center-line C, measured in a direction
parallel to the portions of the plates above the center-line C as
shown in FIG. 7, is a fixed proportion, approximately one third, of
the total dimension Y of the block in this direction. This ratio of
X to Y holds for all the blocks.
The resultant force acting on the block E has a compressive
component F acting through the center of pressure of E and at right
angles to the plate A. This compressive component F sets up a
reaction F' acting through the center of pressure of the adjacent
block G. It can be seen from the above that the bending moment on
plate A about an axis through B at right angles to the sectioning
plane of FIG. 7 therefore dependent on the perpendicular spacing H
between the lines of action of F and F' which in turn is dependent
on the relative positioning of the centers of pressure of the
adjacent blocks E and G.
As stated above it is well known to reduce this bending moment by
progressively increasing the width of the blocks and plates towards
the apex end of the spring. Because of the set ratio of X to Y
referred to above which governs the position of the center of
pressure of each half block relative to the center-line C by
progressively increasing the width of the plates and blocks at the
apex end of the spring the centers of pressure of the half blocks
are displaced further from the center-line C by varying amounts and
the perpendicular spacing H of the lines of action of F and F' and
their equivalents in the other blocks is reduced, thus resulting in
a reduction in bending moment on the intermediate plates.
In order to take maximum advantage of the benefit resulting from
increasing the width of the blocks and plates it is necessary to
adopt the chevron construction shown in FIG. 8 in which the angle R
is equal to the angle S.
The construction shown in FIG. 8 suffers from the serious drawback
that it is too bulky for most practical applications as a result of
its considerable width. This type of spring also has a tendency to
instability due to limited transverse rate.
By coring-out the apex end of the spring the centers of pressure of
the cored-out half blocks are displaced further from the center
line C so that for a given width of cored-out spring the lines of
action of F and F' and their equivalents in the other blocks are
more closely aligned, and thus the bending moments imposed on the
intermediate plates are lower, than in a solid spring of the same
width.
The redistribution of stress in the spring which results from the
alterations in the positions of the center of pressure of the
spring blocks described above allows a larger proportion of the
load imposed on the axle box to be taken by the portions of the
axle box housing directly connected to the associated chevrons thus
relieving the loading on the central bearing-carrying region of the
housing (see FIGS. 1 and 2). Thus the tendency of the housing to
close in on the bearing under the compressive thrust of the spring
is reduced and the pressure distribution of the bearing
improved.
In addition to reducing the bending moments on the intermediate
plates the cavity can also be designed to regulate the spring
stiffness.
* * * * *