GB1588760A - Creación de Inventos y Patentes con Inteligencia Artificial

GB1588760A – Independent wheel suspensions
– Google Patents

GB1588760A – Independent wheel suspensions
– Google Patents
Independent wheel suspensions

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Publication number
GB1588760A

GB1588760A
GB39117/77A
GB3911777A
GB1588760A
GB 1588760 A
GB1588760 A
GB 1588760A
GB 39117/77 A
GB39117/77 A
GB 39117/77A
GB 3911777 A
GB3911777 A
GB 3911777A
GB 1588760 A
GB1588760 A
GB 1588760A
Authority
GB
United Kingdom
Prior art keywords
wheel
control arm
articulation
point
vehicle
Prior art date
1976-09-24
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)

Expired

Application number
GB39117/77A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Daimler Benz AG

Original Assignee
Daimler Benz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1976-09-24
Filing date
1977-09-20
Publication date
1981-04-29

1977-09-20
Application filed by Daimler Benz AG
filed
Critical
Daimler Benz AG

1981-04-29
Publication of GB1588760A
publication
Critical
patent/GB1588760A/en

Status
Expired
legal-status
Critical
Current

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Classifications

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces

B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected

B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically

B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected

B60G21/055—Stabiliser bars

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G3/00—Resilient suspensions for a single wheel

B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram

B60G3/20—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram all arms being rigid

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G2200/00—Indexing codes relating to suspension types

B60G2200/40—Indexing codes relating to the wheels in the suspensions

B60G2200/46—Indexing codes relating to the wheels in the suspensions camber angle

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G2200/00—Indexing codes relating to suspension types

B60G2200/40—Indexing codes relating to the wheels in the suspensions

B60G2200/462—Toe-in/out

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G2200/00—Indexing codes relating to suspension types

B60G2200/40—Indexing codes relating to the wheels in the suspensions

B60G2200/464—Caster angle

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts

B60G2204/10—Mounting of suspension elements

B60G2204/14—Mounting of suspension arms

B60G2204/148—Mounting of suspension arms on the unsprung part of the vehicle, e.g. wheel knuckle or rigid axle

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts

B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions

B60G2204/422—Links for mounting suspension elements

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60G—VEHICLE SUSPENSION ARRANGEMENTS

B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools

B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs

B60G2206/50—Constructional features of wheel supports or knuckles, e.g. steering knuckles, spindle attachments

Description

PATENT SPECIFICATION
( 21) Application No 39117/77 ( 22) Filed 20 Sept 1977 O ( 31) Convention Application No.
2 642 939 ( 32) Filed 24 Sept 1976 in ( 33) Fed Rep of Germany (DE) m ( 44) Complete Specification published 29 April 1981 ( 51) INT CL 3 B 6 OG 3/18 ( 52) Index at acceptance B 7 D 2 A 2 A 2 A 5 A 3 2 A 5 B 2 A ( 54) INDEPENDENT WHEEL SUSPENSIONS ( 71) We, DAIMLER-BE Nz AKTIENG Es ELLSCHAFT, a Company incorporated under the laws of the Federal Republic of Germany, of Stuttgart-Unterttirkheim, Federal Republic of Germany, do hereby declare the invention, for which we -pray that a Patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: –
The invention relates to an independent wheel suspension for vehicles, particularly but not exclusively for motor vehicles, having a wheel carrier which is articulated between an upper and a lower guide link or control arm and has a fixed pivotal axis with respect to one of the guide links.
It is the underlying aim of the invention to develop such a wheel suspension further from the standpoint of minimum installation space and maximum variability and versatility in use, including more particularly its usefulness as a front axle.
According to the invention there is provided an independent wheel suspension for a vehicle having a wheel carrier pivotally connected to an upper wheel control arm and to a lower wheel control arm which is also pivotally connected to the vehicle, the steering axis of the wheel carrier passing through the pivotal connection between the wheel carrier and the wheel control arms, the upper wheel control arm comprising a connecting link and a guide strut pivotally connected to one another, the connecting link being pivotably connected at one end to the wheel carrier and at its other end being pivotably connected to the lower wheel control arm, a pivot axis for the wheel carrier passing through the points of articulation between the wheel carrier and the lower wheel control arm and between the lower wheel control arm and the connecting link, the movement of the wheel carrier about said pivot axis being controlled by the guide strut which extends between the connecting link and the vehicle.
The construction according to the invention makes wide support bases possible for the links for a comparatively small installation space It further permits considerable independence of the camber variation throughout the spring travel, from the link lengths Lastly, it provides good possibilities 55 with regard to the choice of the steering rolling radius desired in each case, and also permits long negative steering rolling radii, and even with conventional wheel dish configurations it provides possibilities of 60 accommodation both for floating saddle and for fixed saddle brakes.
In another aspect of the invention, it is particularly advantageous if the lower wheel control arm to which the connecting link 65 is connected is oriented rearwardly with refernce to the longitudinal axis or direction of the vehicle, in the form of an inclined link with its povital axis extending obliquely from the outside rear to the 70 inside front -as seen in plan Such a configuration more particularly gives the possbility of bracing the axle as far behind the wheel centre as possible and also the possibility of realsing a toe-in of 20 with 75 longtudinal traction, namely by displacing the oblique link outwards under the influence of the braking force This is particularly advantageous in front axles, in which the design of the steering kinematics 80 is no longer obstructed by the length of possible extended positions in the steering linkage On the contrary, optimisation of the transmission ratio in the steering linkage is possible in order that no increase 85 in the steering wheel forces occurs at greater angles of lock.
The wheel suspension according to this invention makes possible, including more particularly for springs and torsion bar 90 stabilisers, transmission ratios of the order of magnitude of 1, and without the necessity for direct bracing on the wheel carrier.
For front wheel suspensions, in spite of a very wide support base in which the 95 outer point of articulation with the vehicle is located approximately in the wheel plane and the inner point of articulation to the vehicle lies approximately in the region of the longitudinal median plane of the 100 ( 11) 1 588 760 1 588 760 vehicle, a large angle of steering lock can be realised if, the lower guide link or control arm being constructed as an inclined link and the orientation of its pivotal axis being oblique from the outside rear to the inside front at a comparatively shallow angle, the inclined link or control arm has a base part substantially associated with the pivotal axis, and an extension displaced at right angles with reference to the front inner point of articulation, at the outer end of which, preferably located in front of the wheel median plane, a spring and a stabiliser are supported and from which a branch carrying the lower point of articulation of the wheel carrier extends generally in the transverse direction of the vehicle.
With such a configuration the inclined control arm or link leaves adequate clearance even for large angles of lock, more particularly if the connecting link, starting from the upper point of articulation to the whel carrier, is articulated to the lower control arm substantially transversely oriented in the region of the spring support and a tension strut, extending effectively parallel to the forwardly projecting arm of the inclined link, to engage the connecting link close to the upper point of articulation of the wheel carrier is articulated to the vehicle above the lower wheel control arm.
Embodiments of the invention will now be described by way of example and with reference to the accompanying drawings, in which:Figure 1 shows an independent front wheel suspension according to the invention in a somewhat schematic plan view, Figure 2 shows the front wheel suspension of Figure 1 in rear elevation, Figure 3 shows the front wheel suspension of Figure 1 in side elevation, Figure 4 shows, in schematic view, a modified form of a front wheel suspension in which the lower guide link or control arm, constructed as an inclined link, is articulated to the wheel carrier through the drag link or steering arm acting as an intermediate element, Figure 5 shows a simplified side elevation of Figure 4, Figure 6 shows a section along the line VI-VI in Figure 5, Figure 7 shows a modification of the wheel suspension shown in the previous Figures, in which a brake disc is arranged within the wheel carrier and the wheel carrier is constructed with a part projecting radially inwards above the brake disc, Figure 8 shows a view similar to Figure 7, with respect to the position of the brake disc with reference to the wheel carrier, and in which the connecting link articulated to the wheel carrier overhangs the brake disc, Figure 9 shows an embodiment of the invention corresponding to Figures 7 and 8 with reference to the position of the wheel carrier and brake disc, in which the connecting link overhangs the brake disc 70 and has a point of articulation for the tension strut which is offset with reference to the line connecting the points of articulation of the connecting link to the wheel carrier and inclined link, and 75 Figure 10 shows a section along the line X-X in Figure 9.
Figures 1 to 3 illustrate, partly schematically and in simplified form, an independent wheel suspension according to the inven 80 tion for a front axle which comprises a lower guide link or wheel control arm 1 and an upper guide link or control arm 2.
These support, at points of articulation E and F associated with them, the wheel car 85 rier 3, to which the wheel 4 is attached rotatably in customary manner, as shown more particularly in Figure 2, whilst in the illustrated embodiment the wheel carrier and also the -wheel stub axle asso 90 ciated therewith (but not further shown here), and the wheel hub 5 overlapping the latter, to which the brake disc 6 is attached integrally for rotation, are located within the wheel dish 7 This position of the wheel 95 carrier 3 and of its point of articulation E and F together with the brake disc 6 and brake saddle 8 within the wheel dish 7 is possible because, in the wheel suspension according to the invention, only very slight 100 relative movements occur between the wheel carrier 3 and the lower guide link 1 and the upper control arm 2 during spring action The indicated position of the points of articulation E and F furthermore makes 105 it possible in a simple manner, for a slight spread, or camber angle of approximately in this embodiment, as Figure 2 shows, to realise negative steering rolling radii.
The lower guide link or wheel control 110 arm 1 is constituted, in the embodiment of the invention illustrated in Figures 1 to 3, by an inclined link pivotally mounted on the vehicle at the points A and B and, the pivotal axis a-b of which, as seen in plan, 115 is oriented obliquely forwardly and inwardly at an angle of substantially 27 with respect to the wheel axis In rear elevation, the pivotal axis a-b is inclined upwardly and inwardly at an angle of substantially 30 120 to the horizontal In side elevation the inclination of the pivotal axis a-b with refereuce to the horizontal is forwardly and upwardly at substantially 5 .
The inclined member forming the lower 125 wheel control arm 1 consists of a base part 9 extending substantially parallel to the pivotal axis a-b, which in conformity with the position of the points of articulation, A and B extends virtually across half the 130 1 588760 width of the vehicle, because the point of articulation A is located close to the longitudinal median line 10 of the vehicle, whereas the point of articulation B falls virtually in the median plane 11 of the wheel 4.
Projecting forward from the base part 9, the control arm 1 has an arm 12 which, as a rough approximation extends perpendicularly to the pivot axis a-b and at the front end of which, close to the transverse median plane 13 of the wheel 4, a suspension spring 14, which in this embodiment is a coil spring, is braced against the lower guide link In this embodiment the point of support of the spring 14 upon the arm 12 lies in’ front of the transverse median plane 13 and due to the distance of the point of support of the spring 14 on the control arm 1 from the pivotal axis a-b a spring transmission ratio of virtually 1 is obtained.
Extending outwards transversely from the arm 12, the lower wheel control arm 1 has an extension 15, so that a basic shape of approximately U-shaped configuration in plan is obtained for the lower control arm, which permits large angles’ of lock because the arm 12 extends from the base part 9 closer to the point of articulation A than to the point of articulation B. The upper guide link or wheel control arm 2 in this embodiment consists of a connecting link 16 and a guide strut 17.
The connecting link 16 is articulated at the point F to the wheel carrier 3, which is indicated only schematically in Figure 1, and it extends from the point of articulation F obliquely forwards and downwards, whilst it is also articulated at the point C to the lower control arm 1 in the region in front of the transverse median plane 13 ‘ of the wheel In practice, the point C illustrated in Figures 1 to 3; as may be seen more particularly from Figure 1, is located in front of the saddle 18 provided on the lower control arm 1 and supporting the spring 14 With reference to the line joining the points of articulation F and C, the connecting link has, in plan, an inclination of the order of 350 with reference to the transverse plane of the vehicle, whilst it extends obliquely forwards and inwards from F to C In rear elevation as shown in Figure 2, the connecting link is inclined to the horizontal at an angle of approximately 430, whilst it extends obliquely upwardly and outwardly from the point of articulation C to the point of articulation F In the side elevation shown in Figure 3, the connecting link 16 has an upwards and rearward inclination of approximately 350 with reference to the horizontal, from the point of articulation C to the point of articulation F As a resuit of this position of the connecting link 16, the point of articulation C has a position beneath the wheel centre and in front of the transverse median plane 13, which dictates, in plan, for the plane determined 70 by the points of articulation C-E-F of the connecting link 16 and the points of articulation of the wheel carrier 3, a pivotal axis c-e with respect to the lower guide link or wheel control arm 1 which extends in 75 ‘ plan obliquely inwards and forwardly at an angle of approximately 220 with respect to the transverse median plane 13 In rear elevation the axis c-e is inclined at an angle of approximately 160 with reference to the 80 horizontal and extends obliquely upwards and inwards In side elevation of the axis c-e has an inclination of approximately 350 with respect to the horizontal and extends upwards and forwards from point E 85 to point C.
The connecting link 16 is articulated to the tension strut 17, at the point of articulation R The point of articulation of the tension strut to the vehicle is designated D 90 and is located behind the connecting link with reference to the longitudinal direction of the vehicle (Figure 3) The tension strut.
17 extends, in the plan shown in Figure 1, at an angle of approximately 360 to the 95.
transverse median plane, obliquely inwards and rearwardly The orientation of the tension strut 17 in the design position is approximately horizontal, as shown in the side’ elevation of Figure 3 and the rear 100 elevation of Figure 2.
In the embodiment, shown in Figures 1 and 3, an arm 21 of a stabiliser 20, which is U-shaped in plan, is articulated to the guide link or lower control arm 1 105 at the point S close to the point of articulation C of the connecting link 16 on the control arm 1 In the design-position, the stabiliser 20, generally’ considered, then lies approximately at the same height as 110 that of the point of articulation C Due to the fact that the point of articulation S of the stabiliser on the guide link or lower wheel control arm 1 is positioned remotely from the pivotal axis a-b, a very good 115 transmission ratio is obtained In the region of its base 22, the stabiliser 20 is attached by links 23 to the vehicle, in this case to the side members 24, of which, as in the’ case of the wheel suspension and of the 120 steering, only those parts associated with one side of the vehicle are shown The connection of the links 23 to the side members 24 and to the base 22 of the stabiliser 20 is effected through resilient 125 bearings in customary manner.
As clearly shown in Figure 3, a drag link or steering arm 25 which projects somewhat obliquely forwards and downwards from the wheel centre is provided 130 1 588 760 on the wheel carrier 3 The steering arm is connected at the point of articulation K to the track rod 26, which is articulated to the steering-gear arm 27 at the point of articulation L The connection of the steering-gear arm 27 (the steering gear is not further shown) to the steering intermediate lever belonging to the other side of the vehicle, which is not shown further here and is correspondingly arranged and supported, is effected by means of a track rod 28 The steering-gear arm 27, and likewise a steering intermediate lever (not shown) extend counter to the direction of travel and are connected to the steering rod 28 at points T This steering arrangement complements the wheel suspension, more particularly with regard to the provision of favourable steering transmission ratios even for large angles of lock.
As shown in Figure 3, the point of articulation K between drag link 25 and track rod 26 is located, in side elevation, somewhat in front of and beneath the point of articulation C of the connecting link 16 to the guide link or lower wheel control arm 1, so that, generally considered from a practical standpoint, it is located close to the wheel rim circumference approximately in the inner boundary plane of the wheel The track rod 26 extends upwardly and rearwardly at an inclination of approximately 13 as can be seen in the side elevation of Figure 3, and in doing so it connects the points of articulation K-L.
In plan, the track rod 26 in this embodiment has an angle of approximately 300 with reference to the transverse median plane and it extends from the inside (point L) obliquely forwards and outwards (point K) In rear elevation (Figure 2, the track rod 26 is inclined upwards and inwards at approximately 80, the point of articulation K being positioned lower than the point of articulation L.
The spring 14, which is braced to the spring saddle 18 upon the lower control arm 1, surrounds the shock absorber 29 which is arranged centrally within the spring The inclination of shock absorber and spring axis with respect to the vertical, for the present embodiment, is approximately 170 as shown in the side elevation of Figure 3 and approximately 70 as shown in the rear elevation according to Figure 2, the spring axis extending obliquely rearwardly as seen in side elevation and inwards as seen from the rear of the vehicle.
In plan and as shown in Figure 1, the spring axis is at an angle of approximately with respect to the transverse plane of the vehicle and it extends forwards and outwards.
Figure 3 shows that in side elevation the inclination of the spring axis is greater than the inclination of the steering axis, which is inclined at approximately 90 to the vertical The point of articulation E of the lower control arm to the wheel carrier lies virtually in the vertical transverse 70 median plane 13 of the wheel, whereas the point of articulation F of the wheel bracket is offset somewhat to the rear with respect to the upper control arm 2.
Furthermore, both points of articulation 75 E, F of the wheel carrier lie in the hollow of the wheel rim, while the point of articulation E lies proximate to or substantially in the median plane of the wheel 4.
The Figures which follow illustrate further 80 embodiments of an independent wheel suspension according to the invention, and corresponding reference numerals, but designated by an index in each case, are used for identical parts 85 The embodiment of the wheel suspension according to the invention illustrated in Figures 4 to 6, which is shown only highly schematically, differs from that according to Figures 1 to 3 in principle solely in the 90 fact that here the lower point of articulation E of the wheel carrier 3 a to the lower guide link or control arm la does not directly represent the connection between the wheel carrier and the control arm, but 95 the point of articulation E is the connection of the control arm to the drag link or steering arm 25 a which is in turn connected rigidly to the wheel carrier 3 a For this purpose, as shown more particularly 100 in Figures 5 and 6, it is combined with a connecting element 30 a in the form of an oval ring cut away on one longitudinal side, of which the two free arm ends 31 a connect rigidly with corresponding arm ends 105 32 a of the wheel carrier 3 a which is bifurcate in its lower region.
By this means a comparatively simple, largely flat construction of the wheel carrier is possible, and the point of articulation Ea 110 between the wheel carrier 3 a and the lower control arm la can nevertheless be positioned so that the brake disc 6 a lies between said point of articulation and the wheel carrier The brake disc then pro 115 jects, in the region of the point of articulation E and at the level of the lower wheel control arm la, into the centre of the ring a which embraces the brake disc 6 a.
Such a configuration permits a particularly 120 large number of possible constructional variations and hence also adaptation to very different design desiderata and conditions.
With reference to Figure 4, and also 125 to the further following Figures, it may be pointed out once more that the tension strut 17 a (or 17 b or 17 c or 17 d) extends, contrary to the schematic illustration shown here, substantially transversely to the 130 1 588760 plane which is defined by the respective points of articulation between connecting link, wheel carrier and lower wheel control arm.
Whereas in the previous embodiments the brake disc is positioned in convenitonal manner outside the wheel carrier in the hollow of the wheel, Figures 7 to 10 illustrate embodiments which display an inverted arrangement, in which the brake disc is offset inwards, with reference to the -wheel carrier In the embodiments according to Figures 7 and 8, the wheel carriers are designated 3 b and 3 c and the brake discs 6 b and 6 c The reference numerals of the connecting links 16 b and 16 c and of the lower control arms lb and lc conform to this identification The points of articulation of the wheel suspension visible in Figures 7 and 8 are analogously designated by the suffixes b and c respectively.
In the embodiment of Figure 7, the wheel carrier 3 b is cranked inwards at its top end across the brake disc 6 b and the point of articulation Fb between the wheel carrier 3 b and the connecting link 16 b is offset inwards with reference to the disc 6 b This makes possible a wheel suspension with a wide base.
In the embodiment of Figure 8, in contradistinction to the embodiment shown in Figure 7, the point of articulation F, is offset outwards with reference to the brake disc 6 c, whereby a construction with a narrower base and correspondingly small offset of the steering axis with reference to the wheel centre is obtained Nevertheless, a negative steering rolling radius can be realised Such an embodiment would be found convenient more particularly for front wheel drive suspensions.
In spite of the overlap across the brake disc both below and above, sufficiently large brake disc diameters can be realised in the case of the construction according to the invention, because the wheel carrier, and hence also the wheel when springing with reference to the connecting link and to the lower control arm, executes practically no movements, with the result that only very small plays are necessary between the wheel rim and the wheel guide elements mentioned.
A further embodiment of a wheel suspension according to the invention will now be explained with reference to Figures 9 and 10, in which similar reference numerals, but suffixed by the letter d, are used The wheel suspension illustrated in these two Figures, which corresponds to that shown in Figures 7 and 8 with regard to the arrangement of the brake disc 6 d, has been further developed in the sense that the forces introduced into the vehicle through the tension strut 17 d, instead of which a thrust rod could of course also be used within the ambit of the invention, are kept as low as possible For this purpose the point of articulation Rd is arranged at a greater distance with respect to the pivotal 70 axis c-e about which the wheel carrier 3 d with the connecting link 16 d pivots than is the case in the embodiments previously described, in which the tension strut engages the connection link substan 75 tially at the line joining the points of articulation C and F.
This is achieved by associating a transverse member 33 d with the -connecting link 16 d which, whilst being rigidly 80 attached to the connecting link 16 d, is articulated at one end to the lower control arm ld, preferably on the axis c-e, and at the other end at an interval from the connecting link, to the tension strut 17 d at 85 the point Rd Since the point Rd is widely spaced from the axis c-e weaker bracing forces are obtained at the point Dd.
The connection of the transverse member 33 d to the guide link ld is illustrated 90 by way of example in Figure 10 and can be ensured in a simple manner by providing a pin on the control arm 1 d, transversely to the axis c-e, by which the transverse member 33 d is tensioned with inter 95 position of resilient buffers 34 d.

Claims (22)

WHAT WE CLAIM IS: –

1 An independent wheel suspension for a vehicle, comprising a wheel carrier pivotally connected to an upper wheel 100 control arm and to a lower wheel control arm which is also pivotally connected to the vehicle, the steering axis of the wheel carrier passing through the pivotal connection between the wheel carrier and the 105 wheel control arms, the upper wheel control arm comprising a connecting link and a guide strut pivotally connected to one another, the connecting link being pivotably connected at one end to the 110 wheel carrier and at its other end being pivotably connected to the lower wheel control arm, a pivot axis for the wheel carrier passing through the points of articulation between the wheel carrier and the 115 lower control arm and between the lower wheel control arm and the connecting link, the movement of the wheel carrier about said pivot axis being controlled by the guide strut which extends between the connect 120 ing link and the vehicle.

2 An independent wheel suspension according to claim 1, wherein the wheel is steerable.

3 An independent wheel suspension 125 according to claim 1 or claim 2 wherein the pivot axis of the lower wheel control arm is inclined rearwardly and outwardly with respect to the longitudinal axis of the vehicle 130 Us is 1 588760

4 An independent wheel suspension according to any one of the preceding claims wherein the lower wheel control arm is constructed as a three-point wheel control arm, two of said points forming the points of articulation of the lower wheel control arm to the vehicle and the third of said points forming the point of articulation of the wheel carrier to the lower wheel control arm.

An independent wheel suspension according to Claim 4, wherein the threepoint control arm is constructed as an inclined link.

6 An independent wheel suspension according to Claim 4, wherein the rearward outer point of articulation of the lower wheel control arm to the vehicle lies substantially in the longitudinal median plane of the wheel.

7 An independent wheel suspension according to any one of Claims 4 to 6, wherein the forward inner point of articulation of the lower wheel control arm to the vehicle lies in the region of the longitudinal axis of the vehicle.

8 An independent wheel suspension according to any one of Claims 4 to 7, wherein the point of articulation of the connecting link to the lower wheel control arm lies outside a triangle defined by said three points of articulation of said control arm as seen in plan view.

9 An independent wheel suspension according to any one of Claims 4 to 8, wherein the spring is supported on the three-point control arm at a point which lies outside a triangle bounded by the points of articulation of said control arm to the vehicle and the wheel carrier, as viewed in plan.

An independent wheel suspension according to any one of the preceding claims, wherein the point of articulation of the connecting link to the lower wheel control arm lies in the front of a transverse plane containing the wheel axis with reference to the longitudinal direction of the vehicle.

11 An independent wheel suspension according to any one of the preceding claims, wherein the connecting link extends substantially in the transverse direction of the vehicle in plan.

12 An independent wheel suspension according to any one of the preceding claims, wherein the point of articulation of the connecting link to the wheel carrier lies behind the transverse plane of the vehicle containing the wheel centre, with reference to the longitudinal direction of the vehicle.

13 An independent wheel suspension according to any one of claims 1 to 12, wherein the guide strut is articulated to the connecting link at a point adjacent to 65 the wheel carrier.

14 An independent wheel suspension according to any one of claims 1 to 13, wherein the strut is a tension strut and is rearwardly inclined with reference to 70 the longitudinal direction of the vehicle.

An independent wheel suspension according to any one of claims 1 to 14, wherein the guide strut is oriented, in plan, substantially perpendicularly to the pivotal 75 axis of the lower control arm.

16 An independent wheel suspension according to any one of Claims 9 to 15, wherein a spring is braced upon the lower wheel control arm adjacent the point of 80 articulation of the connecting link to the lower wheel control arm.

17 An independent wheel suspension according to any one of Claims 9 to 16, wherein, as seen in plan view, a spring 85 saddle is associated with the lower wheel control arm, which lies substantially between the point of articulation of the connecting link to the lower wheel control arm and the point of articulation of the 90 strut to the vehicle.

18 An independent wheel suspension according to Claim 17, wherein the point of articulation of the wheel carrier to the lower wheel control arm is at substantially 95 the same distance from the pivotal axis of said guide link as the spring saddle.

19 An independent wheel suspension according to Claim 17 or Claim 23, wherein one arm of a stabiliser is articu 100 lated to the lower wheel control arm in the region of the spring saddle.

An independent wheel suspension according to Claim 19, wherein the stabiliser is U-shaped in plan, and lies in 105 front of the lower wheel control arm with respect to the longitudinal axis of the vehicle.

21 An independent wheel suspension according to any one of the preceding 110 claims wherein the axis about which the wheel carrier is pivotable with respect to the lower wheel control arm and the axis about which the lower wheel control arm is pivotable are substantially parallel to 115 each other, as seen in plan view.

22 An independent wheel suspension substantially as hereinbefore described, with reference to the accompanying drawings 120 JENSEN & SON, Agents for the Applicants, 8 Fulwood Place, High Holborn, London, WC 1 V 6 HG.
Chartered Patent Agents.
Printed for Her Majesty’s Stationery Office by The Tweeddale Press Ltd, Berwick-upon-Tweed, 1981.
Published at the Patent Office, 25 Southampton Buildings, London, WC 2 A l AY, from which copies may be obtained.

GB39117/77A
1976-09-24
1977-09-20
Independent wheel suspensions

Expired

GB1588760A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

DE19762642939

DE2642939A1
(en)

1976-09-24
1976-09-24

INDEPENDENT WHEEL SUSPENSION FOR VEHICLES, IN PARTICULAR PASSENGER CARS

Publications (1)

Publication Number
Publication Date

GB1588760A
true

GB1588760A
(en)

1981-04-29

Family
ID=5988708
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB39117/77A
Expired

GB1588760A
(en)

1976-09-24
1977-09-20
Independent wheel suspensions

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US
(1)

US4202563A
(en)

JP
(1)

JPS5912484B2
(en)

DE
(1)

DE2642939A1
(en)

FR
(1)

FR2365453A1
(en)

GB
(1)

GB1588760A
(en)

IT
(1)

IT1089886B
(en)

SE
(1)

SE424844B
(en)

Cited By (2)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

GB2243348A
(en)

1990-03-29
1991-10-30
Nissan Motor
Suspension system for an automotive vehicle wheel

GB2319230A
(en)

1996-11-15
1998-05-20
Daimler Benz Ag
Independent suspension with a wheel carrier supported on a semi-trailing or semi-leading arm via a coupling rod

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* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

DE2844866A1
(en)

1978-10-14
1980-04-30
Volvo Car Bv

SUSPENSION FOR A STEERING VEHICLE FRONT WHEEL

EP0052663B1
(en)

1980-11-14
1984-06-27
Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3
Independent suspension for non-steered wheels of motor vehicles exhibiting a camber variation during suspension movement, especially for passenger vehicles

JPS6029312A
(en)

1983-07-27
1985-02-14
Mazda Motor Corp
Rear suspension system for automobile

DE3507141A1
(en)

1985-02-28
1986-09-04
Bayerische Motoren Werke AG, 8000 München

WHEEL SUSPENSION FOR STEERING WHEELS, IN PARTICULAR FRONT WHEELS, OF MOTOR VEHICLES

DE3514815A1
(en)

1985-04-24
1986-11-06
Bayerische Motoren Werke AG, 8000 München

INDEPENDENT VEHICLE WHEEL SUSPENSION

DE3514823A1
(en)

1985-04-24
1986-11-06
Bayerische Motoren Werke AG, 8000 München

INDEPENDENT WHEEL SUSPENSION FOR MOTOR VEHICLES

DE3640931A1
(en)

1986-11-29
1988-06-09
Deere & Co

SUSPENSION OF A STEERING WHEEL

JPS6418710A
(en)

1987-07-13
1989-01-23
Fuji Heavy Ind Ltd
Suspension for automobile

JPH0723285Y2
(en)

1987-08-07
1995-05-31
本田技研工業株式会社

Front wheel suspension

DE3730212A1
(en)

1987-09-09
1989-03-30
Bayerische Motoren Werke Ag
Independent wheel suspension for motor vehicles

DE3929390A1
(en)

1989-09-05
1991-03-07
Bayerische Motoren Werke Ag
Independent wheel suspension for vehicle – has wheel support with upper and lower cross linkage member with upper member actuating connecting pad

DE9090175U1
(en)

1989-12-15
1992-02-06
Yorozu Mfg. Corp., Yokohama, Kanagawa, Jp

US5496055A
(en)

1992-04-28
1996-03-05
Honda Giken Kogyo Kabushiki Kaisha
Suspension system for steered wheel

DE19756065A1
(en)

1997-12-17
1999-07-01
Daimler Chrysler Ag

Independent suspension with a wheel carrier supported by a coupling rod

DE19756064B4
(en)

1997-12-17
2005-08-04
Daimlerchrysler Ag

Independent wheel suspension for front wheels of a motor vehicle with a wheel carrier pivotable for steering purposes

DE102004005811A1
(en)

2004-02-06
2005-09-01
Audi Ag

Stabilizer device of a vehicle

DE602004014339D1
(en)

2004-04-01
2008-07-24
Ford Global Tech Llc

Device for a steerable suspension of a vehicle wheel

DE102004020073B4
(en)

2004-04-24
2013-05-29
Bayerische Motoren Werke Aktiengesellschaft

Vehicle front axle with dissolved lower handlebar level

DE102006004959B4
(en)

2006-02-01
2010-04-22
Zf Friedrichshafen Ag

Wheel suspension for a motor vehicle

US8882116B2
(en)

2006-10-23
2014-11-11
University Of North Carolina At Charlotte
Passive vehicle suspension system providing optimal camber gain

DE102006061975B4
(en)

2006-12-21
2008-11-20
Zf Friedrichshafen Ag

Arm

DE102015203632A1
(en)

2015-03-02
2016-09-08
Zf Friedrichshafen Ag

Independent suspension with high steering angle

DE102017113708A1
(en)

2017-06-21
2018-12-27
Dr. Ing. H.C. F. Porsche Aktiengesellschaft

Suspension for the rear axle of a vehicle

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Assignee
Title

US2094582A
(en)

1934-06-06
1937-10-05
Chapman James Judson
Actuating mechanism for wheel suspensions and the like

FR937309A
(en)

1946-12-11
1948-08-13

Independent wheel suspension system ensuring a constant track for motor vehicles

FR1199213A
(en)

1956-03-20
1959-12-11

Suspension with two conjugate expandable pivoting linkage systems, in particular for motor vehicle wheels

US2866651A
(en)

1956-06-29
1958-12-30
Charles L Powell
Vehicle wheel suspension means

DE1555348A1
(en)

1962-03-02
1970-08-13
Armes De Guerre Fab Nat

Torsion bar suspension for the suspension of vehicles

US3115349A
(en)

1962-05-31
1963-12-24
Gen Motors Corp
Independent front wheel suspension

US3161419A
(en)

1962-12-19
1964-12-15
Gen Motors Corp
Independent wheel suspension linkage

DE1286413B
(en)

1963-10-12
1969-01-02
Daimler Benz Ag

Wheel suspension for the steerable front wheels of motor vehicles

GB1168991A
(en)

1965-07-26
1969-10-29
Humber Ltd
Improvements in or relating to Suspension Systems for Motor Vehicles

GB1198350A
(en)

1967-08-16
1970-07-08
Daimler Benz Ag
Improvements relating to Rear Axle Suspensions

DE1630340C3
(en)

1967-08-16
1973-11-15
Daimler-Benz Ag 7000 Stuttgart

Rear suspension for motor vehicles

DE1755113C3
(en)

1968-03-30
1979-01-18
Daimler-Benz Ag, 7000 Stuttgart

Suspension of steerable front wheels of motor vehicles

DE2137757C3
(en)

1971-07-28
1981-05-07
Charles F. Deerfield Ill. Parsons Jun.

Wheel suspension for motor vehicles, in particular sports cars

DE2151963A1
(en)

1971-10-19
1973-04-26
Porsche Kg

SUSPENSION OF NON-STEERED, DRIVEN BIKES FOR VEHICLES, IN PARTICULAR FOR MOTOR VEHICLES

DE2233391C3
(en)

1972-07-07
1980-01-03
Alfred Teves Gmbh, 6000 Frankfurt

Wheel suspension for the steered wheels of motor vehicles

DE2255679A1
(en)

1972-11-14
1974-05-30
Daimler Benz Ag

INDEPENDENT SUSPENSION OF THE FRONT WHEELS OF MOTOR VEHICLES

DE2264300B2
(en)

1972-12-30
1975-09-18
Daimler-Benz Ag, 7000 Stuttgart

Front suspension for passenger cars

DE2439365C3
(en)

1974-08-16
1979-06-07
Bayerische Motoren Werke Ag, 8000 Muenchen

Wheel suspension for motor vehicles, in particular for passenger cars

1976

1976-09-24
DE
DE19762642939
patent/DE2642939A1/en
active
Granted

1977

1977-09-13
IT
IT50998/77A
patent/IT1089886B/en
active

1977-09-20
GB
GB39117/77A
patent/GB1588760A/en
not_active
Expired

1977-09-22
JP
JP52113410A
patent/JPS5912484B2/en
not_active
Expired

1977-09-22
FR
FR7728609A
patent/FR2365453A1/en
active
Granted

1977-09-23
SE
SE7710708A
patent/SE424844B/en
not_active
IP Right Cessation

1977-09-26
US
US05/836,614
patent/US4202563A/en
not_active
Expired – Lifetime

Cited By (6)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

GB2243348A
(en)

1990-03-29
1991-10-30
Nissan Motor
Suspension system for an automotive vehicle wheel

US5102159A
(en)

1990-03-29
1992-04-07
Nissan Motor Co., Ltd.
Suspension system for automotive vehicle wheel

GB2243348B
(en)

1990-03-29
1994-02-02
Nissan Motor
Suspension system for automotive vehicle wheel

GB2319230A
(en)

1996-11-15
1998-05-20
Daimler Benz Ag
Independent suspension with a wheel carrier supported on a semi-trailing or semi-leading arm via a coupling rod

GB2319230B
(en)

1996-11-15
1999-08-25
Daimler Benz Ag
Independent suspension with a wheel carrier supported on a semi-trailing arm via a coupling rod

US5984329A
(en)

1996-11-15
1999-11-16
Daimlerchrysler Ag
Independent wheel suspension having a wheel carrier supported via a coupling rod on a semi-trailing arm

Also Published As

Publication number
Publication date

SE424844B
(en)

1982-08-16

SE7710708L
(en)

1978-03-25

DE2642939A1
(en)

1978-03-30

JPS5343326A
(en)

1978-04-19

FR2365453B1
(en)

1982-05-28

US4202563A
(en)

1980-05-13

DE2642939C2
(en)

1987-05-27

FR2365453A1
(en)

1978-04-21

JPS5912484B2
(en)

1984-03-23

IT1089886B
(en)

1985-06-18

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