DE102017207803A1 - A pivot bearing for an axle assembly of a heavy duty vehicle, axle assembly having such a pivot bearing and heavy duty vehicle having at least one such axle assembly - Google Patents

Abstract

The invention relates to a pivot bearing (12) designed and intended to be used in an axle assembly of a heavy duty vehicle (80), comprising a base unit (30) adapted for connection to the heavy duty vehicle (80), for connection to the rotating assembly (34) formed on the base unit (30) rotatable relative to the base unit (30) about an axis of rotation (A) and a bearing assembly (57) disposed between the base unit (30) and the rotary unit (34); both for the transmission of forces acting in the direction of the axis of rotation (A) between the base unit (30) and the rotary unit (34) and for the transmission of radial forces acting between the base unit (30) and the radial axis (A) the rotary unit (34) is designed and determined. According to the invention, the bearing arrangement (57) is designed as a plain bearing and comprises at least one axially and / or radially directed plain bearing section (40, 46).

Description

The invention relates to a pivot bearing, which is designed and intended to be used in an axle assembly of a heavy duty vehicle, comprising a formed for the connection with the not belonging to the rotary bearing heavy load vehicle and certain base unit, one for connection to the also not belonging to the pivot bearing axle assembly trained and certain rotary unit, which is rotatably mounted on the base unit relative to this about a rotation axis, and arranged between the base unit and the rotary unit bearing arrangement, both for transmitting forces acting in the direction of the axis of rotation between the base unit and the rotary unit and for transmission is formed and determined in relation to the axis of rotation in the radial direction acting forces between the base unit and the rotary unit,
The heavy-duty vehicle may be both a motor-driven heavy-duty vehicle and a passively trailing heavy-duty vehicle, for example a heavy-duty trailer or as specified in Annex XI to EC Directive 2007-46-EC, as amended on 15.07.2011, a "trailer for heavy-duty transports". that is, according to the definition given there, a class O4 vehicle for the transport of indivisible loads (for example rotor blades of wind turbines) subject to speed and traffic restrictions due to their dimensions, including hydraulic modular trailers, irrespective of the number of modules , It should also be noted that even with the motor-driven heavy-duty vehicle not every of the axle assemblies needs to be driven by a motor.

Moreover, only such heavy duty vehicles are considered to be heavy duty vehicles within the meaning of the present invention in which the load for which each individual axle assembly is designed has a value of at least 5 tons, preferably at least 6 tons.

One problem which must always be considered in the design of such heavy duty vehicles are the conflicting demands on the one hand for the largest possible loading height above the loading area and on the other for a long stroke of at least 40 cm, preferably at least 50 cm, more preferably at least 60 cm, between the maximum spring-down condition and the maximum rebound condition, so that the heavy-duty vehicle can drive through depressions and negotiate smaller obstacles without the cargo bed having to change its orientation relative to the horizontal.

It goes without saying that this problem can be tackled most effectively if the top of the tires in the maximum compression state of the axle assembly has the smallest possible distance from the loading surface, i. if as little height as possible is lost by the construction of the heavy-duty vehicle. In this regard, tower pivot bearings are advantageous because they can dive into the space between the two tires of the axle assembly space and do not interfere with the space between the cargo area and the top of the tire.

However, especially in the context of pendulum-axis axle assemblies, these tower bearings have the disadvantage that they limit the pendulum motion of the axle assemblies at medium compression states in which they dive into the existing between the two tires of the axle assembly space. In contrast, a very large freedom from oscillations offer turntables, which are arranged substantially in the existing between the top of the tires and the loading space space. However, these turntables limit the freedom from commuting with heavy deflection. Furthermore, it is easy to see that these slewing rings are also disadvantageous with respect to the loading height and stroke path problems explained above.

It is therefore an object of the present invention to provide a rotary bearing of the type mentioned above, which compared with a turntable improved loading height-stroke characteristics and optionally compared with a tower bearing has improved freedom from commuting.

This object is achieved by a pivot bearing of the type mentioned, in which the bearing assembly is designed as a sliding bearing and at least one axially and / or radially directed sliding bearing portion comprises.

It is the merit of the inventor to have recognized that due to the low speeds or rotational speeds that occur during steering movements of heavy-duty vehicles, the use of plain bearings in the pivot bearings of axle assemblies is possible. Slide bearings have the advantage over rolling bearings the advantage of a lower overall height in the power transmission direction, since they generally have a higher load carrying capacity. If, therefore, sliding bearings are used both for the transmission of forces acting in the direction of the axis of rotation and for the transmission of forces acting in the radial direction relative to the axis of rotation, then the pivot bearing has the same overall load bearing capacity both in the axial direction and in the radial direction of smaller dimensions as a rolling bearing.

The smaller dimensions give the axle assembly greater freedom in pendulum motion. In addition, the load height stroke characteristics of the axle assembly are improved. Optionally, the smaller dimensions in the radial direction may even result in the pivot bearing not interfering with the space available between the bed of the heavy duty vehicle and the top of the axle assembly tires, further improving the load height stroke characteristics of the axle assembly.

To enable the transmission of forces, which are exerted by the weight of the arranged on the bed of the heavy load vehicle charge, it is advantageous if a substantially associated with the base unit sliding surface portion of a sliding bearing portion above a rotating unit associated sliding surface portion of this plain bearing portion is arranged and thus applied under the weight of the load against the rotary unit associated sliding surface section.

Of course, it is desirable that the axle assembly is reliably held on the heavy vehicle even during compression. In order to make this possible, it is further proposed that the bearing arrangement comprises at least one further sliding bearing section, wherein, with a substantially vertically oriented rotational axis, a sliding surface section of this further sliding bearing section assigned to the base unit is arranged below a sliding surface section of this further sliding bearing section associated with the rotary unit. Since this additional plain bearing section only has to be able to carry the weight of the axle assembly, it can be sized correspondingly small. In principle, however, nothing speaks against the fact that the surface areas of the sliding surface sections of the one slide bearing section and of the further slide bearing section are of equal size. Since the one slide bearing portion and the other slide bearing portion extend at a predetermined distance from the rotation axis, they are also able to transmit tilting moments.

With regard to its function of weight transfer, the one sliding bearing section or / and the further sliding bearing section can be arranged axially directed, i. his or her surface normal points in a direction parallel to the axis of rotation.

As can be seen from the above discussion, at least one slide bearing section can also have a radial surface component and / or be arranged radially directed in order to be able to transmit cornering forces and / or tilting moments.

With regard to the cylinder symmetry predetermined by the rotational movement of the axle assembly around the axis of rotation, it is advantageous if the one slide bearing section and / or the further slide bearing section are substantially annular. According to the radially directed or the radial surface component having sliding bearing portion may be formed substantially cylindrical.

In principle, it is conceivable that the mutually associated sliding surface sections abut each other directly. According to the invention, however, it is preferred that at least one sliding element is arranged between the mutually associated sliding surface sections of at least one sliding bearing section. In this context, it may further be provided that the at least one sliding element is fastened to one of the sliding surface sections, for example by gluing. However, it is also conceivable that the at least one sliding element is arranged to be freely movable between the two sliding surface sections.

In a further development of the invention, the sliding element or the sliding elements can be produced using polytetrafluoroethylene (PTFE). In this case, the PTFE may be reinforced by means of a fabric that is produced, for example, using glass fibers and / or aramid fibers. For example, a silicone adhesive can be used for the optional bonding of the sliding element to one of the sliding surface sections.

Furthermore, in a further development of the invention, the at least two adjacent sliding bearing sections associated sliding elements may be formed as a one-piece sliding element.

Finally, the sliding element or the sliding elements can be protected by the provision of sealing elements from external influences. These sealing elements may comprise at least one O-ring and / or at least one lip seal element.

In other aspects, the invention relates to an axle assembly, in particular a pendulum axle assembly comprising a pivot bearing according to the invention and a heavy duty vehicle having at least one such axle assembly.

• 1 eine grob schematischen und perspektivische Ansicht eines Schwerlastfahrzeugs, bei welchem wenigstens eine Achsbaugruppe mit einem erfindungsgemäßen Drehlager ausgerüstet ist;
• 2 eine Schnittansicht einer ersten Ausführungsform eines erfindungsgemäßen Drehlagers; und
• 3 eine Schnittansicht einer zweiten Ausführungsform eines erfindungsgemäßen Drehlagers.

The invention will be explained in more detail below with reference to the accompanying drawings in two exemplary embodiments. It shows:

• 1 a rough schematic and perspective view of a heavy-duty vehicle, in which at least one axle assembly is equipped with a pivot bearing according to the invention;
• 2 a sectional view of a first embodiment of a pivot bearing according to the invention; and
• 3 a sectional view of a second embodiment of a pivot bearing according to the invention.

In 1 are a heavy duty vehicle according to the invention 80 and its framework 82 roughly schematically shown by dashed lines. The heavy truck 80 has a plurality of axle assemblies 10 of which in 1 one is shown in detail.

The axle assembly 10 includes a pivot bearing 12 by means of which it is rotatable about a substantially vertical axis A with the vehicle frame 82 of the heavy vehicle 80 connected is. The axle assembly 10 further includes one with the pivot bearing 12 firmly connected bogie 14 , at the free end of a swingarm 16 is arranged. The swingarm 16 is on the bogie 14 about a substantially horizontally extending axis B pivotally mounted. At her from the bogie 14 distant end points the swingarm 16 a (not shown) bearing neck on which one with tires 21 fitted wheel carrier 20 is mounted pivotably about a pendulum axis C.

The bogie 14 and the swingarm 16 also have a power device 22 in contact with each other. The strength device 22 is executed in the embodiment shown here as a fluid-actuated piston-cylinder unit. One end of the power device 22 is with the bogie 14 about a joint 24 articulated while the other end of the strength device 22 with the swingarm 16 also via a joint 26 articulated is connected.

The pivot bearing 12 , the bogie 14 and the swingarm 16 together form a bogie 18 by means of which the wheel carrier 20 in the sense of leveling the vehicle frame 82 can be approximated and removed from this (pivoting movement about the axis B), in the sense of steering the heavy vehicle 80 can be rotated about the vertical axis A, and in the sense of a compensation of unevenness of the running surface S about the pendulum axis C can be pivoted.

It should be added that the wheel carrier 20 against rotational or pivotal movements about other axes than the pendulum axis C with the rocker 16 or with the pivot bearing 12 opposite, free end of the axle 18 is rigidly connected.

With reference to the 2 includes the pivot bearing 12 a base unit 30 , which by means of bolts 32 at the frame 82 of the heavy vehicle 80 is attached. The base unit 30 is rotationally symmetrical with respect to the axis of rotation A and has a substantially cylindrically shaped main portion 30a and a substantially annular side section 30b on. With her side section 30b lies the base unit 30 at the bottom of the vehicle frame 82 at.

Furthermore, the pivot bearing includes 12 a turntable 34 , which is also rotationally symmetrical with respect to the axis of rotation A. The turntable 34 has a substantially cylindrically shaped main portion 34a and a substantially annular side section 34b on. The main section surrounds 34a the turntable 34 the main section 30a the base unit 30 coaxial, while the minor section 34b the turntable 34 below the secondary section 30b the base unit 30 is arranged.

In the cylindrical gap 36 between the main section 30a the base unit 30 and the main section 34a the turntable 34 is a cylindrical sliding element 38 taken, which together with the surface 30 a1 of the main section 30a and the surface 34a1 of the main section 34a a radially directed sliding bearing section 40 forms. The plain bearing section 40 This is mainly used for cornering forces and tilting moments of the axle assembly 10 take.

In an analogous manner is in the annular gap 42 between the secondary section 30b the base unit 30 and the minor section 34b the turntable 34 an annular sliding element 44 taken, which together with the surface 30b1 of the auxiliary section 30b and the surface 34b1 of the subsection 34b an axially directed sliding bearing section 46 forms. The plain bearing section 46 The main purpose of this is to reduce the weight on the truck bed 82a of the heavy vehicle 80 to pick up static charge and to the axle assembly 10 forward.

Furthermore, one removes 2 that the base unit 30 also a final plate 48 comprising, which by means of bolts 50 at the main section 30a the base unit 30 is attached. Between a radially outer edge portion 48a the end plate 48 and the main section 34a the turntable 34 is an annular gap 52 formed, in which a substantially annularly shaped sliding element 54 is arranged. The sliding element 54 forms together with the surface 34a2 of the main section 34a the turntable 34 and the surface 48a1 of the border section 48a the end plate 48 a further axially directed sliding bearing section 56 ,

The slide bearing sections 40 . 46 and 56 together form a bearing assembly 57 ,

It should also be noted that the sliding element 38 in a depression 30a2 of the main section 30a the base unit 30 and a depression 34a3 of the main section 34a the turntable 34 is recorded in order to keep it in the desired position during operation. In an analogous way, the sliding element 44 in a depression 30b2 of the secondary section 30b the base unit 30 and a depression 34b2 of the secondary section 34b the turntable 34 received, and is the sliding element 54 in a depression 34a4 of the main section 34a the turntable 34 and a depression 48a2 of the border section 48a the end plate 48 added.

In 3 a second embodiment of a pivot bearing according to the invention is shown, which essentially according to the first embodiment 2 equivalent. Therefore, in 3 Analog parts provided with the same reference numerals as in 2 , but increased by the number 100 , In addition, the pivot bearing 112 according to 3 in the following will be described only insofar as it is from the pivot bearing 12 according to 2 which is otherwise expressly referred to the description thereof.

The pivot bearing 112 according to 3 is different from the pivot bearing 12 according to 2 only by the formation of the sliding elements and their arrangement between the main section 130a the base unit 130 and the main section 134a the turntable 134 , between the side section 130b the base unit 130 and the minor section 134b the turntable 134 , as well as between the edge section 148a the end plate 148 and the main section 134a the turntable 134 , And that are the sliding elements 158 and 160 not in wells of the base unit 130 and the turntable 134 recorded in order to remain in the desired position during operation. Rather, both have sliding elements 158 and 160 each a substantially cylindrical section 158a respectively. 160a and a substantially annular portion 158b respectively. 160b on, which are integrally formed with each other to form fit between the base unit 130 and the turntable 134 to be held.

The two substantially cylindrical sections 158a and 160a take over the function of the same element 38 the embodiment according to 2 while the section 158b the function of the sliding element 44 according to 2 and the section 160b the function of the sliding element 54 according to 2 take.

It is still to be added that the sliding elements 158 and 160 also with the base unit 130 or the turntable 134 can be glued. This variant can also with the sliding elements 38 . 44 and 54 the embodiment according to 2 be used, in which case the arrangement of the sliding elements in the recesses of the base unit 30 or the turntable 34 It is possible to dispense with the production of the basic unit 30 and the turntable 34 simplified.

It should also be added that the sliding elements of both embodiments can advantageously be produced from fabric-reinforced polytetrafluoroethylene (PTFE), wherein the reinforcing fabric can be formed, for example, from glass fibers and / or aramid fibers. As an adhesive, for example, a silicone adhesive can be used.

After all, it should also be added that the gap between the base unit 30 respectively. 130 and the turntable 34 respectively. 134 in which the sliding elements 38 . 44 . 54 respectively. 158 . 160 are received, both in the embodiment according to 2 as well as in the embodiment according to 3 by sealing elements 62 respectively. 162 is protected from external influences.

Claims (15)

A pivot bearing (12) adapted and intended to be used with an axle assembly (10) of a heavy duty vehicle (80), comprising: a base unit (16) designed and defined for connection to the heavy truck (80) not belonging to the pivot bearing (12) 30), a for connection to the also not to the pivot bearing (12) associated with the axle assembly (10) formed and certain rotation unit (34) which is rotatably mounted on the base unit (30) relative to this about a rotation axis (A), and a between the base unit (30) and the rotary unit (34) arranged bearing assembly (57), both for transmitting in the direction of the axis of rotation (A) acting forces between the base unit (30) and the rotary unit (34) as well as for the transmission of related formed and determined on the axis of rotation (A) acting in the radial direction forces between the base unit (30) and the rotary unit (34), characterized in that the bearing arrangement (57) as Slide bearing is designed and at least one axially and / or radially directed sliding bearing portion (40, 46). Turning bearing after Claim 1 characterized in that at substantially vertically oriented axis of rotation (A) associated with the base unit (30) sliding surface portion (30b1) of a sliding bearing portion (46) above one of the rotary unit (34) associated Gleitflächenabschnitts (34b1) of this sliding bearing portion (46) is arranged. Turning bearing after Claim 1 or 2 , characterized in that the bearing arrangement (57) comprises at least one further slide bearing section (56), wherein at substantially vertically oriented axis of rotation (A) one of the base unit (30) associated sliding surface portion (48a1) of this further slide bearing portion (56) below one of the rotary unit (34) associated sliding surface portion (34a4) of this further sliding bearing portion (56) is arranged. Turning bearing after Claim 2 or 3 , characterized in that the one sliding bearing portion (46) and / or the further sliding bearing portion (56) is arranged axially directed or are. Swivel bearing according to one of the Claims 2 to 4 , characterized in that the one slide bearing portion (46) and / or the further slide bearing portion (56) are formed substantially annular. Swivel bearing according to one of the Claims 1 to 5 , characterized in that at least one sliding bearing portion (40) has a radial surface component and / or is arranged radially directed and preferably Turning bearing after Claim 6 , characterized in that the radially directed or the radial surface component having sliding bearing portion (40) is formed substantially cylindrical. Swivel bearing according to one of the Claims 2 to 7 , characterized in that between the mutually associated Gleitflächenabschnitten at least one sliding bearing portion (40, 46, 56) at least one sliding element (38, 44, 54) is arranged. Turning bearing after Claim 7 characterized in that the sliding member (38, 44, 54) is fixed to one of the sliding surface portions (30a1, 30b1, 48a1). Turning bearing after Claim 8 or 9 , characterized in that the sliding elements (158a, 158b or 160a, 160b) associated with at least two adjacent sliding bearing sections are formed as an integral sliding element (158 or 160). Swivel bearing according to one of the Claims 1 to 10 , characterized in that the sliding element or the sliding elements is protected by the provision of sealing elements (62) from external influences or are Swivel bearing according to one of the Claims 1 to 11 characterized in that at least one slide bearing portion (46) is mounted in a state mounted between the truck bed (82a) of the heavy duty vehicle (80) and the top of the axle assembly tires (21) on a heavy duty vehicle (80) and axle assembly (10). 10) existing space is arranged. Swivel bearing according to one of the Claims 1 to 12 , characterized in that at least one sliding bearing portion (40) in a state mounted on the heavy load vehicle (80) and the axle assembly (10) in the space between the two tires (21) of the axle assembly (10) can be accommodated. Axle assembly (10), in particular pendulum axle axle assembly (10), with a pivot bearing (12) according to one of Claims 1 until 1113 Heavy goods vehicle (80) with at least one axle assembly (10) according to Claim 14 ,

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