DE102017111779A1 - Independent wheel suspension for a steerable wheel - Google Patents

Abstract

The invention relates to an independent suspension (20) for a steerable wheel (16) of a motor vehicle (10), in particular a mobile agricultural machine, preferably a crop protection syringe. The independent wheel suspension (20) comprises a gantry gearbox (34) having a housing (36) and a drive shaft (32) drivingly connected to the gantry gearbox (34). The independent wheel suspension (20) comprises a first transverse link (24) articulated to the housing (36) of the gantry gear (34) and a second transverse link (26) articulated to the housing (36) of the gantry gear (34). is connected.

Description

The invention relates to an independent suspension for a steerable wheel of a motor vehicle, preferably a sprayer.

Conventional agricultural vehicles are usually equipped with simple and robust rigid axles. The front axles usually have a pendulum joint to improve off-road capability. The rear axles often have to dispense with any suspension for reasons of traction optimization. For some individual cases, however, it makes sense to equip the trolleys with suspension systems, also for reasons of soil conservation. Thus, independent wheel suspensions for agricultural vehicles are known from the prior art. These offer over rigid axles the advantage that there is no mutual influence of the suspension on both sides of the vehicle.

An example of an independent suspension for an agricultural train, transport or special vehicle is in the EP 2 965 928 A1 disclosed. The independent suspension comprises a steering column which cooperates via a fork bridge with a linear guide which is movable in an approximately vertical direction, the fork bridge producing a steering connection pivotable about an approximately vertical axis of rotation to a vehicle frame. Further, the linear guide is coupled to a fluidic damping element, which forms a supporting part of the fork bridge. The damping element comprises a damping cylinder, which is designed as a steering column. Furthermore, the damping element has one or more pressure reservoirs with connections, wherein the pressure reservoirs are fluidically connected to the damping cylinder via line systems. The wheel is driven by a hydraulic wheel hub motor.

Another example of an independent suspension is in the WO 2010 020 607 A1 disclosed. This independent suspension is designed as a double wishbone independent suspension. As a drive for the wheels, a hydraulic wheel hub motor is used.

To increase the ground clearance, it is also known to use portal axles. Agricultural vehicles with portal axles and gantry gears are, for example, in the EP 3 061 640 A1 and the EP 3 061 332 A1 disclosed.

The various systems for independent suspension each have different advantages and disadvantages in terms of complexity, functionality and controllability.

The invention is based on the object to provide an improved independent suspension that overcomes disadvantages of the prior art and / or provides additional advantages in terms of complexity, functionality and / or controllability.

The object is achieved by an independent suspension according to the independent claim. Advantageous developments are specified in the dependent claims and the description.

The independent wheel suspension is intended for a steerable wheel of a motor vehicle, in particular a mobile agricultural machine, preferably a plant protection syringe. The independent suspension has a gantry with a housing. The independent suspension has a drive shaft which is drivingly connected to the gantry gear on. The independent suspension has a first arm, which is pivotally connected to the housing of the gantry gear, and a second control arm, which is pivotally connected to the housing of the gantry on.

The combination of mechanical drive, gantry gearbox, first wishbone and second wishbone allows the advantages of the respective components in an independent suspension to be largely reconciled. The independent suspension offers increased ride comfort, good tunability, a robust mechanical final drive and a high ground clearance.

In particular, the drive shaft may be included in a mechanical drive train and / or driven by a differential gear, in particular a transverse differential.

Preferably, the first wishbone may be an upper wishbone and the second wishbone may be a lower wishbone. The first transverse link may in particular be arranged above the second transverse link.

The terms "upper" and "lower" used herein refer to an installation position of the respective component in the motor vehicle.

In a preferred embodiment, the first wishbone and / or the second wishbone is designed as a wishbone. Alternatively or additionally, the first transverse link and the second transverse link together form a double wishbone, in particular a double wishbone. Alternatively or additionally, the first transverse link and / or the second transverse link is formed in one, in particular asymmetrical, arc shape. The wishbone provide sufficient rigidity against longitudinal forces and also allow a space-saving arrangement of other components of the Independent suspension between the legs of the wishbone.

In a further embodiment, the drive shaft is designed as a propeller shaft, in particular a synchronizing shaft. Alternatively or additionally, the drive shaft is pivotally connected to a drive element of the portal transmission. Alternatively or additionally, the drive shaft is pivotally connected to an output element of a differential gear, in particular a transverse differential, connectable. The embodiment as a propeller shaft has the advantage that an angular offset between the driving element and the driven element can be compensated. The constant velocity shaft has the advantage that no nonuniformity is generated in the transmission of the rotational movement, even if bending angles occur at the joint of the propeller shaft.

In one embodiment, a first joint connects the first transverse link and the housing of the portal transmission. The first joint allows pivotal movement between the first control arm and the housing of the gantry gear to steer the wheel. Alternatively or additionally, a second joint connects the second transverse link and the housing of the portal transmission. The second joint allows pivotal movement between the second control arm and the housing of the gantry gear to steer the wheel.

In a further development, the first joint additionally allows a tilting movement between the first transverse link and the housing of the portal transmission. A tilting axis of the tilting movement extends obliquely, in particular perpendicularly, to a pivot axis of the pivoting movement between the first transverse link and the housing of the gantry transmission. Alternatively or additionally, the second joint additionally allows a tilting movement between the second control arm and the housing of the gantry transmission. A tilting axis of the tilting movement extends obliquely, in particular perpendicularly, to a pivot axis of the pivoting movement between the second transverse link and the housing of the gantry transmission.

In an advantageous development, the first joint and / or the second joint simultaneously allows a steering movement of the wheel and a spring movement of the independent suspension. Thus both movements can be covered by the first joint and / or the second joint.

In a preferred embodiment, the first joint and / or the second joint is designed as a ball joint. The ball joint allows both pivoting movements for steering the wheel and tilting movements for shock absorption or height level adjustment.

In a further embodiment variant, the first joint and the second joint define a steering axle of a steering knuckle steering of the independent wheel suspension.

In one embodiment, the housing of the gantry gear on a first projection area. In particular, the first protruding portion may extend from a main body portion of the housing of the gantry gear in a direction to the first transverse link. At the first projection portion, the first joint is attached. The provision of a protruding portion for the first hinge allows a large turning angle for steering the wheel which is not limited by the main body portion.

In particular, the first projection region may have a support surface on which the first joint is mounted, and / or a neck region which connects the support surface to the main body region. Preferably, the neck region in a horizontal plane may have a U-shaped cross-section which is open towards the drive shaft.

In a further embodiment, the housing of the gantry gear has a second projection region, which in particular extends from a main body region of the housing of the gantry transmission in a direction to the second transverse link. At the second projecting portion, the second joint is attached. The provision of a protruding portion for the second hinge allows a large turning angle for steering the wheel which is not limited by the main body portion.

In a further embodiment, the independent suspension further comprises a tie rod for connection to a steering cylinder. The tie rod is articulated, in particular via a ball joint, connected to the housing of the portal transmission. Preferably, a joint for connecting the tie rod with the housing of the gantry gear on a facing in the direction of travel or against the direction of travel side surface of the housing of the portal gear is mounted. About a steering cylinder can thus be directed by means of the tie rod connected to the gantry gear wheel.

In a further embodiment variant, the drive shaft is arranged between the first transverse link and the second transverse link, in particular with respect to a vertical axis. Alternatively or additionally, the drive shaft may be arranged between the first projection region and the second projection region, in particular with respect to a vertical axis. This allows a space-saving design and also a large steering angle formed as a drive shaft drive shaft.

In another embodiment, the independent suspension comprises a damping device connected to the housing of the gantry transmission for shock absorption, and / or a height level adjustment device connected to the housing of the gantry transmission for adjusting a height level of the independent suspension. In particular, the damping device and the height level adjustment device can be designed as an integrated unit, preferably as a hydropneumatic cylinder. Thus, depending on the training shock absorption, a height level adjustment or an integrated shock absorption and height level adjustment can be made.

In a development, the first transverse link has a first leg and a second leg. The damping device, the height level adjustment device and / or the integrated damping and height level adjustment device is arranged between the first leg and the second leg. As a result, a space-saving arrangement is made possible.

Advantageously, the damping device, the height level adjustment device and / or the integrated damping and height level adjustment means articulated, in particular via a ball joint on the second wishbone, preferably a facing in the direction of travel or against the direction of travel side surface of the second control arm attached.

In a further embodiment, the gantry gear has a drive element to which the drive shaft is connected, and / or an output element for connection to the wheel. Alternatively or additionally, the first transverse link, the second transverse link and / or the integrated damping and height level adjustment device can be attached to a frame component of the motor vehicle.

The invention further relates to a motor vehicle, in particular a mobile agricultural machine, preferably a sprayer. The motor vehicle has a first axis and a second axis, wherein, in particular, the first axis and the second axis, for example via a lockable longitudinal differential, are mutually lockable. The motor vehicle also includes an independent suspension as disclosed herein that is integrated with the first axle and / or the second axle.

• 1 eine Seitenansicht einer Pflanzenschutzspritze;
• 2 eine perspektivische Vorderansicht einer lenkbaren Einzelradaufhängung mit mechanischem Antrieb;
• 3 eine perspektivische Rückansicht der lenkbaren Einzelradaufhängung mit mechanischem Antrieb;
• 4 eine Draufsicht auf die lenkbare Einzelradaufhängung mit mechanischem Antrieb;
• 5 eine perspektivische Vorderansicht einer Lenkvorrichtung mit teilweiser Darstellung der Einzelradaufhängung;
• 6 eine perspektivische Rückansicht der Lenkvorrichtung mit teilweiser Darstellung der Einzelradaufhängung;
• 7 eine perspektivische Vorderansicht der Lenkvorrichtung; und
• 8 eine Schnittansicht durch ein Portalgetriebe der lenkbaren Einzelradaufhängung.

The preferred embodiments and features of the invention described above can be combined with one another as desired. Further details and advantages of the invention will be described below with reference to the accompanying drawings. Show it:

• 1 a side view of a sprayer;
• 2 a front perspective view of a steerable independent suspension with mechanical drive;
• 3 a rear perspective view of the steerable independent suspension with mechanical drive;
• 4 a plan view of the steerable independent suspension with mechanical drive;
• 5 a front perspective view of a steering device with partial representation of the independent suspension;
• 6 a rear perspective view of the steering device with partial representation of the independent suspension;
• 7 a front perspective view of the steering device; and
• 8th a sectional view through a portal gear of the steerable independent suspension.

The embodiments shown in the figures are at least partially identical, so that similar or identical parts are provided with the same reference numerals and to the explanation of which reference is also made to the description of the other embodiments or figures in order to avoid repetition.

The 1 shows a trained as a mobile agricultural vehicle motor vehicle 10 in which the device according to the invention can be used. In detail, in the example shown, the motor vehicle 10 designed as a sprayer, in which the device according to the invention can be used particularly advantageously. However, those skilled in the art will recognize that other mobile agricultural machines or motor vehicles may use the apparatus of the present invention.

The car 10 has a front axle 12 and a rear axle 14 on. The front axle 12 carries two wheels 16 and the rear axle 14 carries two wheels 16 of which in the side view of 1 only one is visible at a time. The wheels 16 are each on a wheel hub 18 assembled. The front axle 12 and the rear axle 14 can be locked to each other via a Längsverteilergetriebe (not shown). The front axle 12 and the rear axle 14 can be designed as portal axles to increase the ground clearance.

The independent suspension disclosed herein, the steering device disclosed herein, and / or the gantry gear disclosed herein may be in the front axle, for example 12 of the motor vehicle 10 be integrated.

With reference to the 2 and 3 Below is an exemplary steerable independent suspension 20 described. The independent suspension 20 has a mechanical drive train 22 , a first wishbone 24 and a second control arm 26 on. In addition, the independent suspension 20 a damping and height level adjustment device 28 and the wheel hub 18 on.

The wheel hub 18 is from the mechanical drive train 22 driven. The mechanical drive train 22 has a transverse differential 30 , a drive shaft 32 and a portal gearbox 34 on. The wheel hub 18 and the portal gearbox 34 form a stub axle of a stub axle steering the independent suspension 20 , which uses the so-called Ackermann geometry.

The transverse differential 30 distributes the driving force provided by a motor to the left and right wheels of an axle (for example, the front axle 12 , please refer 1 ). The engine may be, for example, an internal combustion engine, for example a diesel engine, an electric motor or a hydraulic motor. The engine can be used in particular as a central drive unit for all driven wheels 16 (please refer 1 ) be provided. The transverse differential 30 drives the drive shaft 32 in turn, via the portal gearbox 34 the wheel hub 18 drives. The drive shaft 32 is designed as a propeller shaft, in particular a synchronizing shaft. In detail, the drive shaft 32 articulated with an output element of the transverse differential 30 and hinged with an input member of the portal transmission 34 connected. The portal gearbox 34 has a housing 36 on. An exemplary construction of the portal transmission 34 will be described later herein with reference to FIGS 8th described.

The mechanical drive train 22 provides a robust mechanical final drive. When using a longitudinal distributor, the front axle 12 and the rear axle 14 be executed lockable to each other (see 1 ). This can be ensured that the driving force on the front axle 12 and the rear axle 14 divided, for example, in the ratio 50%: 50% (mechanical lock). When using one or more hydraulic drive units, this would be very expensive possible. A transfer of full engine power would only be possible by using large engines. Mechanical axle drives also offer good efficiency.

The first wishbone 24 and the second wishbone 26 are designed as a wishbone and thus form a double wishbone.

The first wishbone 24 has an arc shape. The arch shape is asymmetric, ie both legs of the arch are not mirror-symmetrical (see 4 ). The first (upper) wishbone 24 is about a joint 38 (Ball joint) hinged to the housing 36 of the portal transmission 34 connected. The joint 38 is at a first, upper projection area 40 of the housing 36 assembled.

The first projection area 40 extends from a main body area 42 of the housing 36 towards the first wishbone 24 , The first projection area 40 forms an upper area of the housing 36 , In the main body area 42 are the gears of the portal transmission 34 added. The first projection area 40 has a support surface 40A on, on which the joint 38 is mounted. The first projection area 40 has a neck area 40B on top of the support surface 40A with the main body area 42 combines. The neck area 40B has a U-shaped cross section in a horizontal plane, which is in the direction of the drive shaft 32 is open.

The first wishbone 24 is about two more joints 44 connected to a frame member (not shown). The other joints 44 For example, they can be designed as radial ball joints, which can be attached to the frame component via through-holes in protruding bolts.

The second wishbone 26 has an arch shape with an extended tip area. The arch shape is asymmetric, ie both legs of the arch are not mirror-symmetrical (see 4 ). The second (lower) wishbone 26 is about a joint 46 (Ball joint) articulated with a second projection area 48 of the housing 36 connected. The second projection area 48 extends from the main body portion 42 towards a vehicle centerline. The second wishbone 26 is about two more joints 50 connected to a frame member (not shown). The joints 50 For example, like the joints 44 be constructed.

The joints 38 . 46 allow a pivoting movement between the respective wishbone 24 . 26 and the housing 36 of the portal transmission 34 for steering the wheel. In particular, the wheel may be around one of the joints 38 . 46 Defined steering axle of a stub axle steering of the independent suspension 20 be steered.

In addition, allow the joints 38 . 46 a tilting movement between the respective control arm 24 . 26 and the housing 36 , The tilt axis is perpendicular to the pivot axis. Thus, from the joints 38 and 46 also spring movements of the housing 36 covered.

The drive shaft 32 is between the first wishbone 24 and the second transverse link 26 arranged with respect to a vertical axis. In particular, an output element of the drive shaft 32 between the first projection area 40 and the second protrusion area 48 arranged. The connection to the portal gearbox 34 takes place in the U-shaped neck area 40B of the housing 36 , This allows a space-saving arrangement of the components of the independent suspension 20 ,

The integrated damping and height level adjustment device 28 For example, it is designed as a hydro-pneumatic cylinder. The device 28 is about a joint 52 (see, for example. 3 ), for example a ball joint, on the second transverse link 26 appropriate. In detail, the device 28 on a side facing in the direction of travel or against the direction of travel side surface of the control arm 26 hinged. In other embodiments, for example, only one damping device may be provided and / or one damping device may be provided separately from a height level adjustment device. At one of the joints 52 opposite end of the device 28 can the decor 28 hingedly attached to a frame member (not shown).

The device 28 is arranged so that it is between a first leg 24A and a second leg 24B of the first transverse link 24 extends. The two thighs 24A . 24B are connected together at one end, at an opposite end of the respective leg 24A . 24B spaced apart and thus form the arched shape of the first arm 24 ,

On a side of the main body area facing in the direction of travel or against the direction of travel 42 of the housing 36 is a joint 54 assembled. At the joint 54 can a tie rod (not shown in the 2 and 3 ) to be assembled. The tie rod allows for axle steering around the joints 38 . 46 defined steering axle. The joint 54 can on a facing in the direction of travel or against the direction of travel side surface of the main body portion 42 be mounted.

With reference to the 4 . 5 and 6 is below a steering device 56 the independent suspension 20 described.

The steering device 56 has a steering cylinder 58 , a first intermediate link 60 and a second intermediate member 62 on. The steering device 56 also has a first connection component 64 , a second connecting member 65 , a first tie rod 66 and a second tie rod 68 on.

The steering cylinder 58 is as a synchronous cylinder with a first piston rod 70 and a second piston rod 72 educated. The steering cylinder 58 has a cylinder housing 73 on. The first piston rod 70 and the second piston rod 72 are retractable and extendable in the cylinder housing 73 stored. In detail, the first piston rod 70 opposite to the second piston rod 72 retractable and retractable. In particular, the first piston rod extend 70 and the second piston rod 72 from opposite sides of a piston surface in the cylinder housing 73 , The first piston rod 70 and the second piston rod 72 are connected to each other via the piston surface and thus coupled in their movements. A retraction of the first piston rod 70 leads to an extension of the second piston rod 72 and vice versa. The first piston rod 70 and the second piston rod 72 may be formed as separate components or as an integral unit, for example, together with the piston surface. The steering cylinder 58 can be designed as a hydraulic cylinder. Hydraulic fluid can, for example, via hydraulic connections 75 to or from the cylinder housing 73 be directed.

At opposite ends of the piston rods 70 . 72 are the intermediate links 60 . 62 attached. This moves the intermediate links 60 . 62 along with the movement of the piston rods 70 . 72 , The intermediate links 60 . 62 are about the connection components 64 . 65 connected with each other. The first intermediate link 60 , the connecting components 64 . 65 and the second intermediate member 62 engage around the ends of the first and second piston rod 70 . 72 U-shaped.

The first tie rod 66 is about the joint 54 hinged to the housing 36 of the portal transmission 34 connected. The second tie rod 68 is correspondingly connected to a housing of a portal transmission on the other longitudinal side of the motor vehicle (not shown).

The first tie rod 66 is hinged to the first link 60 about a joint 74 , in particular a radial ball joint, attached. The second tie rod 68 is hinged to the second intermediate member 62 about a joint 76 , in particular a radial ball joint, attached. In detail, the first tie rod 66 at the first intermediate member 60 mounted at a position relative to the end of the first piston rod 70 is offset. Likewise, the second tie rod 68 to the second intermediate member 62 mounted at a position relative to the end of the second piston rod 72 is offset.

In particular, the intermediate links 60 . 62 designed so that a distance between the opposite ends of the piston rods 70 . 72 is greater than a distance between the joints 74 . 76 , These are the joints 74 . 76 in a radial direction with respect to a longitudinal axis of the piston rods 70 . 72 offset to the piston rods 70 . 72 , In addition, the joints 74 . 76 in a direction parallel to the longitudinal axis of the piston rods 70 . 72 with respect to the respective ends of the piston rods 70 . 72 offset from each other. In other words, the joints 74 . 76 are with respect to a vertical axis under the piston rods 70 . 72 arranged and offset with respect to a vehicle transverse axis (front axle longitudinal direction) toward a vehicle central axis (center of axle).

To enable the staggered arrangement of the joints 74 . 76 extends the first intermediate member 60 from the end of the first piston rod 70 in one direction to the second tie rod 68 , Likewise, the second intermediate member extends 62 from the end of the second piston rod 72 in a direction to the first tie rod 66 ,

The arrangement of the joints 74 . 76 allows in conjunction with the wishbones 24 . 26 a space-saving construction of an Ackermann geometry (axle steering). In particular, the arrangement and dimensioning of the wishbone 24 . 26 and the tie rod 66 each a parallelogram, so that during a spring movement of the independent suspension 20 no steering movement arises. Thus, there is no change in track during a spring movement.

However, those skilled in the art will recognize that the staggered arrangement of a joint of a tie rod with respect to one end of a piston rod of a steering cylinder can be used with only one piston rod in steering cylinders designed as differential cylinders. Thus, for example, comparable advantages can be achieved.

The joints 74 . 76 are at the connection components 64 . 65 attached. In particular, screws (not shown) extending through through holes in the pontics 60 . 62 extend into threads of the connecting components 64 . 65 screwed. For example, a first screw (not shown) is through a through hole 74A a connection end 74B of the joint 74 and a through hole of the first intermediate member 60 in an internal thread of the first connecting member 64 screwed in (see 7 ). This is the tie rods 66 . 68 over the joints 74 . 76 and screws (not shown) extending through through holes in the pontics 60 . 62 extend, at the pontics 60 . 62 appropriate.

The first connection component 64 is designed as a guide rod. The second connection component is designed as a rod. A longitudinal guide 78 leads the first connection component 64 during a movement caused by an extension of the piston rod 70 or 72 is effected. The longitudinal guide 78 points to a pipe element 80 on, in which the first connection component 64 is slidably mounted. The longitudinal guide 78 leads the first connection component 64 in a direction parallel to a longitudinal axis of the steering cylinder 58 , The longitudinal guide 78 is on the cylinder housing 73 attached.

In other embodiments, for example, instead of two connection components, only one longitudinally guided connection component may be provided.

To maximize the travel distance of the piston rods 70 . 72 to allow to have the intermediate links 60 . 62 one recess each 60A . 62A on. The recesses 60A . 62A are to an outer shape of the cylinder housing 73 customized. Thus, the cylinder housing 73 when fully retracting the first piston rod 70 partly in the recess 60A of the first intermediate link 60 be recorded. On the other hand, the cylinder housing 73 during complete retraction of the second piston rod 72 partly in the recess 62A of the second intermediate member 62 be recorded.

The steering cylinder 58 brings the required steering force to steer the housing 36 of the portal transmission 34 and the wheel hub 18 on. In addition, the steering cylinder supports 58 the unevenly introduced over the wheels forces. The steering forces are via the tie rods 66 . 68 transfer. Over the wheels introduced forces are on the tie rods 66 . 68 in the connecting components 64 . 65 initiated. Through the longitudinal guide (linear guide) 78 In addition, lateral forces can be absorbed and an anti-rotation lock of the steering cylinder 58 be enabled. About the intermediate links 60 . 62 the forces are in the steering cylinder 58 transfer.

With reference to 8th is below the gantry gearbox 34 described in more detail. The portal gearbox 34 has an input shaft 82 , an intermediate wave 84 and an output shaft 86 on. The portal gearbox 34 additionally has a first (input side) spur gear stage 88 and a second (output side) spur gear stage 90 on.

The input shaft 82 , the intermediate shaft 84 and the output shaft 86 are rotatable in the housing 36 stored. An input element 92 of portal transmission 34 is articulated with the drive shaft 32 (not in 8th shown; please refer 2 ) connectable. The input element 92 is non-rotatable with the input shaft 82 connected. The drive shaft 32 drives the input element 92 which in turn is the input shaft 82 drives (turns).

On the input shaft 82 is a drive gear 94 the input-side spur gear 88 arranged rotationally fixed. On the intermediate shaft 84 is an output gear 96 the input-side spur gear 88 arranged rotationally fixed. The drive gear (pinion) 94 and the output gear 96 comb each other. The input shaft 82 drives the drive gear 94 which, in turn, the output gear 96 drives (turns). The output gear 96 drives the intermediate shaft 84 at.

On the intermediate shaft 84 is a drive gear 98 the output side spur gear 90 arranged rotationally fixed. On the output shaft 86 is an output gear 100 the output side spur gear 90 arranged rotationally fixed.
The drive gear (pinion) 98 and the output gear 100 comb each other. The intermediate shaft 84 turns the drive gear 98 which in turn is the output shaft 86 over the output gear 100 drives (turns).

The output shaft 86 drives the wheel hub 18 which in turn is the wheel 16 (not shown in 8th ; please refer 1 ) turns. With the wheel hub 18 are a brake pot 102 and a brake disc 104 connected to the wheel hub 18 rotate.

In detail, thus, the transverse differential 30 , the drive shaft 32 , the input element 92 , the input shaft 82 , the input-side spur gear 88 , the intermediate shaft 84 , the output side spur gear 90 , the output shaft 86 and the wheel hub 18 connected in this order.

The input-side spur gear stage 88 and the output side spur gear stage 90 For example, they may have a common translation of i≥7. A large gearing ratio allows the drive shaft to transmit only a small amount of torque at a high speed, so the drive shaft does not have to be designed to transmit large torques.

The input-side spur gear stage 88 is with respect to the output side spur gear stage 90 outwardly (ie, in a direction opposite to a vehicle center longitudinal axis) offset. In other words, the input side spur gear is 88 offset to the output side spur gear 90 on a bike 16 (please refer 1 ) facing side of the output-side spur gear 90 arranged. This allows the input element 92 be positioned comparatively far outside, so that more space for the trained as a propeller shaft drive shaft 32 (not shown in 8th ; please refer 2 ) is available.

The arrangement of the components (gears, shafts) of the portal transmission 34 also includes that the output gear 96 in a direction perpendicular to a longitudinal axis of the output shaft 86 considered at least partially overlapping with the output shaft 86 is arranged. Likewise, the input shaft 82 in a direction perpendicular to a longitudinal axis of the intermediate shaft 84 considered at least partially overlapping with the output side spur gear 90 arranged.

The input shaft 82 is also in a direction perpendicular to a longitudinal axis of the output shaft 86 considered overlapping with the output shaft 86 arranged. The input element 92 is also in a direction perpendicular to the longitudinal axis of the intermediate shaft 84 considered partially overlapping with the output side spur gear 90 and the output shaft 86 arranged. In addition, the output gear is 96 between the output side spur gear 90 on the one hand and the brake disc 104 , the brake pot 102 , the wheel hub 18 and the wheel 16 (please refer 1 ) On the other hand arranged.

The portal gearbox 34 shows the case 36 with the main body area 42 and the projection areas 40 . 48 on. In addition, the housing has 36 a tapered area 106 on. The rejuvenating area 106 tapers in one direction to the wheel hub 18 , The rejuvenating area 106 surrounds the output shaft 86 , The rejuvenating area 106 extends from a hub side (right side in 8th ) of the output gear 96 and a hub side (right side in FIG 8th ) of the output gear 100 towards the wheel hub 18 , The rejuvenating area 106 is determined by the relative to the output side spur gear 90 outwardly offset input-side spur gear 88 allows. The rejuvenating area 106 allows a space-saving arrangement of the brake disc 104 and the brake pot 102 that the rejuvenating area 106 in a circumferential direction about the output shaft 86 surround. The brake pot 102 also tapers between the brake disc 104 and the wheel hub 18 in one direction to the wheel hub 18 ,

By the arrangement of the output side spur gear 90 on an inside of the portal gear 34 becomes a slim case 36 allows. This will provide sufficient space for the brake disc 104 created and a simple shot the bearing of the output shaft 86 outside possible.

The invention is not limited to the preferred embodiments described above. Rather, a variety of variants and modifications is possible, which also make use of the inventive idea and therefore fall within the scope. In particular, the invention also claims protection of the subject matter and the features of the subclaims independently of the claims referred to.

LIST OF REFERENCE NUMBERS

10

motor vehicle

12

First axle (front axle)

14

Second axle (rear axle)

16

wheel

18

wheel hub

20

independent suspension

22

Mechanical drive train

24

Upper (first) wishbone

24A

First leg

24B

Second thigh

26

Lower (second) wishbone

28

Damping and height level adjustment device (hydro-pneumatic cylinder)

30

transverse differential

32

drive shaft

34

portal transmission

36

Housing of the portal transmission

38

Joint (ball joint)

40

First projection area

40A

support surface

40B

neck

42

Main body portion

44

Joint (radial ball joint)

46

Joint (ball joint)

48

Second projection area

50

Joint (radial ball joint)

52

Joint (ball joint)

54

Joint (ball joint)

56

steering device

58

steering cylinder

60

First intermediate link

60A

recess

62

Second intermediate link

62A

recess

64

First connection component

65

Second connecting component

66

First tie rod

68

Second tie rod

70

First piston rod

72

Second piston rod

73

cylinder housing

74

Joint (radial ball joint)

74A

Through Hole

74B

connecting end

75

hydraulic connection

76

Joint (radial ball joint)

78

longitudinal guide

80

tube element

82

input shaft

84

intermediate shaft

86

output shaft

88

Input side spur gear

90

Output side spur gear

92

input element

94

Drive gear (pinion)

96

output gear

98

Drive gear (pinion)

100

output gear

102

brake pot

104

brake disc

106

Rejuvenating area

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 2965928 A1 [0003]
• WO 2010020607 A1 [0004]
• EP 3061640 A1 [0005]
• EP 3061332 A1 [0005]

Claims (15)

Independent wheel suspension (20) for a steerable wheel (16) of a motor vehicle (10), in particular a mobile agricultural machine, preferably a plant protection syringe, comprising: a gantry gear (34) having a housing (36); a drive shaft (32) drivingly connected to the gantry gear (34); a first transverse link (24) articulated to the housing (36) of the gantry gear (34); and a second transverse link (26) articulated to the housing (36) of the gantry gear (34). Independent suspension (20) to Claim 1 wherein: the first transverse link (24) and / or the second transverse link (26) is designed as a wishbone; and / or the first transverse link (24) and the second transverse link (26) together form a double wishbone, in particular a double wishbone; and / or the first transverse link (24) and / or the second transverse link (26) is formed in an, in particular asymmetric, arch shape. Independent suspension (20) to Claim 1 or Claim 2 wherein the drive shaft (32): as a propeller shaft, in particular a synchronizing shaft is formed; and / or hingedly connected to a drive element of the gantry transmission (34); and / or articulated with an output element of a differential gear (30), in particular a transverse differential, is connectable. Independent wheel suspension (20) according to one of the preceding claims, wherein: a first joint (38) connecting the first transverse link (24) and the housing (36) of the gantry gear (34) and a pivoting movement between the first transverse link (24) and the housing (36) of the portal gear (34) for steering the wheel ( 16); and or a second hinge (46) interconnects the second transverse link (26) and the housing (36) of the gantry gear (34) and pivotal movement between the second transverse link (26) and the housing (36) of the gantry gear (34) for steering the wheel (Fig. 16). Independent suspension (20) to Claim 4 in which: the first joint (38) additionally permits tilting movement between the first transverse link (24) and the housing (36) of the gantry gear (34), a tilting axis of the tilting movement being inclined, in particular perpendicular, to a pivot axis of the pivoting movement between the first Wishbone (24) and the housing (36) of the gantry gear (34) extends; and / or the second joint (46) additionally allows a tilting movement between the second transverse link (26) and the housing (36) of the gantry gear (34), wherein a tilting axis of the tilting movement obliquely, in particular perpendicular, to a pivot axis of the pivoting movement between the second Wishbone (26) and the housing (36) of the gantry gear (34) extends. Independent suspension (20) to Claim 4 or Claim 5 wherein the first joint (38) and / or the second joint (46) simultaneously allows a steering movement of the wheel (16) and a spring movement of the independent suspension (20). Independent suspension (20) according to one of Claims 4 to 6 wherein: the first joint (38) and / or the second joint (46) is formed as a ball joint; and / or the first hinge (38) and the second hinge (46) define a steering axle of a kingpin steering of the independent wheel suspension (20). Independent suspension (20) according to one of Claims 4 to 7 in that: the housing (36) of the gantry gear (34) has a first protrusion portion (40) to which the first hinge (38) is secured and which, preferably, extends from a main body portion (42) of the housing (36) of the gantry gear (34) extends in a direction to the first transverse link (24); and / or the housing (36) of the gantry gear (34) has a second protruding portion (48) to which the second hinge (46) is secured and which, preferably, extends from a main body portion (42) of the housing (36) of the gantry gear (34) extends in a direction to the second transverse link (26). Independent wheel suspension (20) according to one of the preceding claims, further comprising: a track rod (66) for connection to a steering cylinder (58), wherein the track rod (66) is articulated, in particular via a ball joint, to the housing (36) of the portal gear (34), wherein, preferably, a joint (54) for connecting the tie rod (66) with the housing (36) of the gantry gear (34) on a facing in the direction of travel or against the direction of travel side surface of the housing (36) of the gantry gear (34) is mounted. Independent wheel suspension (20) according to one of the preceding claims, wherein: the drive shaft (32) is arranged between the first transverse link (24) and the second transverse link (26), in particular with respect to a vertical axis; and / or the drive shaft (32) between the first projection portion (40) and the second Projection region (48), in particular with respect to a vertical axis, is arranged. Independent wheel suspension (20) according to one of the preceding claims, further comprising: a damping device which is connected to the housing (36) of the portal gear (34) for shock absorption; and or a height level adjusting device connected to the housing (36) of the gantry gear (34) for adjusting a height level of the independent wheel suspension (20), wherein, in particular, the damping device and the height level adjustment device are formed as an integrated unit (28), preferably as a hydropneumatic cylinder. Independent suspension (20) to Claim 11 wherein: the first transverse link (24) has a first leg (24A) and a second leg (24B); and the attenuator, the height level adjuster, or the integrated attenuation and height level adjuster (28) is disposed between the first leg (24A) and the second leg (24B). Independent suspension (20) to Claim 11 or Claim 12 wherein the damping device, the height level adjustment device or the integrated damping and height level adjustment device (28) articulated, in particular via a ball joint, on the second wishbone (26), preferably a facing in the direction of travel or against the direction of travel side surface of the second control arm (26) attached is. Independent wheel suspension (20) according to one of the preceding claims, wherein: the portal gear (34) has a drive element to which the drive shaft (32) is connected and / or an output element for connection to the wheel (16); and or the first transverse link (24), the second transverse link (26) and / or the integrated damping and height level adjustment device (28) can be attached to a frame component of the motor vehicle (10). Motor vehicle (10), in particular mobile agricultural machine, preferably plant protection syringe, with: a first axis (12) and a second axis (14), wherein, in particular, the first axis (12) and the second axis (14), for example via a lockable longitudinal differential, are mutually lockable; and an independent wheel suspension (20) according to one of the preceding claims, which is integrated in the first axle (12) and / or the second axle (14).

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