ES2762213T3 - Sliding door module / pivot door module for a rail vehicle with at least two guide carriages / guide slides for each door leaf - Google Patents

Abstract

Sliding door module / pivoting and sliding door module (1) for a vehicle on rails comprising: - at least one door leaf (2), - a support (3) oriented longitudinally in the direction of insertion of the door leaf (2), which is slidably housed in a horizontal direction, in particular transversely to its longitudinal extension, - a linear roller guide with at least one profiled rail (15), the at least one profiled rail (15) being fastened on the support (3) or being comprised by it in the form of a profiled area, and - at least two separate guide carriages / guide slides (4), in particular spaced from each other in the insertion direction of the door leaf (2 ), which are associated only with a door leaf (2), with which the door leaf (2) is slidably housed, characterized in that - the linear roller guide has several guide carriages / guide slides ( 4) with rotation of c Rolling bodies, where the guide carriages / guide slides (4) are housed on the at least one profiled rail (15), - the guide lengths (f) of the guide carriages / guide slides (4) are in sum, at most half as long as the distance (g) of the external contact points (10, 11), which have the guide carriages / guide slider (4) that support the door leaf (2) with the profiled rail (15), and - the guide carriages / guide slides (4) associated with a door wing (2) are joined - rigidly, - in an articulated manner or - partially rigidly, partially articulated with a cross beam (5) that supports the door leaf (2) or with the door leaf (2).

Description

DESCRIPTION

Sliding door module / pivot door module for a rail vehicle with at least two guide carriages / guide slides for each door leaf

The invention relates to a sliding door module / sliding and pivoting door module for a rail vehicle, as described in the preamble of claim 1 and as known from the state of the art according to DE 715057 C .

Sliding door modules / pivot and sliding door modules of the mentioned type are fundamentally known. In this regard, generally one door leaf or two door leafs are slidably housed, which firstly swing outwards for opening in the case of a pivoting and sliding door module with the help of an extension mechanism and then move , or in the case of a sliding door module only move. In order to ensure smooth running, the door wings are generally accommodated with the help of linear roller guides. These linear roller guides are fundamentally known from the construction of machine tools in which the exact guidance of machine parts is essential. These, therefore, are designed as far as possible without play and require a comparatively rigid substructure to avoid unwanted tension of the linear roller guides and guarantee a long service life. The constructions used according to the state of the art are therefore also designed comparatively rigid, so that shocks that act on the vehicle on rails are transmitted practically abruptly on the sliding door module / sliding and pivoting door module. As a result, the useful life of the linear guide is reduced again. Furthermore, the known solutions are comparatively complicated and consequently have a negative impact on the total weight of the vehicle on rails. In particular, in urban traffic where rail vehicles accelerate over short distances and again brake, such load-bearing construction worsens the energy efficiency of the rail vehicle.

Therefore, an object of the invention is to indicate an improved sliding door / pivot door module. In particular, the above described disadvantages must be avoided or their repercussions must at least be mitigated. Furthermore, the main objective of the invention is to ensure the smooth running of the guide carriages / guide slides with rotation of rolling bodies in the case of a sliding door module / pivoting and sliding door module also with comparative flexing. more intense of the support or the profiled rails.

The object of the invention is solved with a sliding door module / pivoting and sliding door module having the characteristics of the characterizing part of claim 1.

In this regard, the linear roller guide has several guide carriages / guide slides with rotation of rolling bodies, the guide carriages / guide slides being housed on the at least one profiled rail. In this regard the guide lengths of the guide carriages / guide slides are in total no more than half as long as the total guide length, that is, the distance between the external contact points, which the guide carriage has / guide slide that supports the door wing with the profiled rail. Thus, the accommodation of the guide carriages / guide slides also in the case of comparatively strong flexing of the support or the profiled rail remains smooth. In the case of the linear roller guide with rotation of rolling bodies, the guide length and the total guide length can be referred to the external rolling bodies that the door wing supports. Furthermore, the guide carriages / guide slides associated with a door wing are rigidly, hingedly or partially rigidly, partially hingedly connected to a cross beam supporting the door wing or to the door wing. In the case of a rigid connection of the guide carriages / guide slides with the cross beam / door wing, a simple and robust construction of the sliding door module / pivoting and sliding door module is produced. If the guide carriages / guide slides are jointed with the cross beam / door swing in an articulated manner, a flexing of the support can be compensated to a better since the guide carriages / guide slides can follow a local orientation of the support or of the guide rail and the risk of unwanted tension of the linear guide is reduced thereby. By making a partially rigid, partially articulated connection of the guide carriages / guide slides to the cross beam / door wing, the load between the guide carriages / guide slides can thus be accurately distributed. A pivotally housed guide / guide slide carriage can absorb virtually no torque about a horizontal axis transverse to its longitudinal axis, while a rigidly attached guide / guide slide carriage can absorb such torque. In the proposed manner the torque caused by the weight of the door leaf can be adequately transmitted to the support due to the guide carriages / guide slides (in particular spaced apart), on the other hand the linear guide due to the relatively long guide length short of the individual guide carriages / guide slides is also less prone to stress. In the supporting construction of the sliding door module / pivot and sliding door module, comparatively large flexures can therefore be allowed. For this reason it is possible to make these relatively light and to improve overall the energy efficiency of the vehicle on rails.

In particular the mentioned guide carriages / guide slides associated only with a door wing, are housed in only one profiled rail. In principle, however, several guide carriages / guide slides can also be associated with a door wing, which are housed on different profiled rails. They can also be spaced from each other in the direction of insertion of the door leaf.

The profiled rails can have a different shape. For example, C-shaped or U-shaped profiled rails, T-shaped profiled rails, profiled rails with circular cylindrical cross-section or for example also profiled rails with essentially rectangular cross-section can be provided. The mentioned cross sections may also have concavities or also convexities. By means of concavities, grooves are simultaneously formed in which rolling bodies can be guided.

Linear roller guides offer good running smoothness with little or no internal bearing clearance, however, due to the high surface pressures between rolling body and profile rail they are very prone to overload, in particular jerking. Due to the soft configuration of the support, however, such shocks are damped very well, whereby the advantage of the invention in using linear roller guides especially arises. Linear roller guides can be realized, for example with balls or rollers as rolling bodies. The rolling bodies form in a contact area the connecting element between the profile rail and the guide carriage. Rolling bodies that are not currently in contact with the profiled rail are driven along a return zone (eg return channel) from the end of the contact zone to its start or vice versa. The rolling bodies therefore move in a closed path. This path is generally arranged essentially in one plane, the "plane of rotation." In this regard, an oval path can be provided, or several successive oval or circular paths are provided, which are arranged in the same plane and completely form a contact area. Furthermore, several paths can also be located on different planes but parallel to each other. Finally, the paths can also intersect. For example, an orbit can leave the plane of rotation in the inversion zone to allow a crossing with another orbit. If necessary, the rolling bodies can also be arranged in a rolling body cage.

At this point it should be noted that the features of the invention are particularly suitable for use in a pivot and slide door or in a pivot and slide door module. However, the invention can also be used for a sliding door or sliding door module in which or in which a pivot mechanism is missing. Other advantageous configurations and improvements of the invention result from the dependent claims, as well as from the description in joint vision with the figures.

It is especially advantageous if the guide carriages / guide slides are oriented on the unloaded cross beam along a course of the longitudinal beam in the loaded operating state. In the state of the longitudinal beam without load, the two guide carriages therefore tension each other, which, however, is not detrimental because these in this state do not move or only little on the profiled rail. If the door leaf is mounted and the support accordingly enters the loaded operating state, then there is virtually no tension on the guide carriages. An articulated housing of the guide carriages can therefore be removed. The transverse beam can in this respect be accepted as rigid, its deformation under load can also be taken into account. In general, therefore, the guide carriages / guide slides are largely guided without tension on the profile rail. Accordingly, the durability of the guide system can be increased considerably.

It is also advantageous if a guide carriage / guide slide associated with the door wing and located close to it are hingedly connected and a guide carriage / guide slide associated with the door wing and located further from it are rigidly connected with the cross beam or the door wing. In particular in this context it is advantageous if at least the closest located guide / guide slide carriage associated with the door wing is hingedly connected and at least the farthest located guide guide / guide slide carriage associated with the door wing. it is rigidly attached to the cross beam or door wing. In an arrangement in which the door wing viewed in the longitudinal direction of the support / insertion direction is cantilevered in the cross beam the nearest located guide / guide slide carriage associated with the door wing without additional measures is to as a general rule withstand a much higher load than the guide carriage / guide slide located farthest from the door leaf. It is advantageous to articulate at least the nearest guide carriage / guide slide the door wing with the cross beam so that it is practically not absorbing any torque transverse to its longitudinal axis. As a compensation, the most remote guide / guide slide carriage is rigidly attached to the cross beam, so that it can absorb said torque. In this way the total load can be well distributed on the individual guide carriages / guide slides. If more than two guide carriages / guide slides are associated with a door wing, then several guide carriages / guide slides can be hingedly or rigidly connected to the cross beam / door wing.

It is especially advantageous in the above context also when an articulated joint is recessed versus a rigid joint with respect to the course of the longitudinal beam, in particular if the recess is relative to the course of the longitudinal beam in the loaded operating state. In this variant of the sliding door module / door module pivoting and sliding to the farthest guide carriage / guide slide is precisely imposed a torque around its transverse axis in which an articulated housed guide / guide carriage is lowered from the course of the longitudinal beam. The cross beam in case of load then forcibly tilts downwards at the point of the guide carriage / guide slide housed in an articulated manner, or is deformed by the load accordingly, whereby the guide carriage / guide slide rigidly housed guide is loaded with a torque. The more intensively the hinged housed guide / guide slide is lowered, the more intensively the rigidly housed guide / guide slide carriage is loaded. In a particularly advantageous variant of the sliding door module / sliding and sliding door module the mentioned recess is relative to the course of the longitudinal beam in the loaded operating state, to a state in which the door wing (s) are mounted. Due to the resulting bending of the longitudinal beam the recess of the hinged housed guide / guide carriage may be somewhat more intense, before a noticeable torque is applied to the rigidly housed guide / guide carriage. transversely to its longitudinal axis. In this model the longitudinal beam for the provision of the mentioned recess although it is loaded and therefore deformed, the transverse beam is however assumed as not loaded. In the case of actual loading, of course the cross beam is also loaded and deformed until the rotating bearing comes into contact.

It is also particularly advantageous if the guide carriages / guide slides associated with a door wing are arranged along an arc or rotated in opposite directions about a horizontal axis and running transversely to the longitudinal extent of the longitudinal beam , wherein the end directed to the door wing of a guide carriage / guide slide located farthest from the door leaf is recessed in front of a guide carriage / guide slide located closest to the door leaf with respect to a course of the longitudinal beam. In other words, the guide carriages / guide slides are rotated in opposite directions more intensively than would be necessary for tension-free guidance on the longitudinal (flexed) beam. In this way, after mounting the system on the longitudinal beam, the cross beam is flexed upward and prestressed, whereby the two guide carriages / guide slide are pulled upwards. The load is therefore reduced by the weight of the door leaf on the guide carriage closest to the door leaf. Consequently the load can be accurately distributed among the guide carriages / guide slides. The aforementioned pre-stress may be relative in this respect to both the unloaded longitudinal beam and the loaded longitudinal beam. Furthermore, a deformation of the cross beam by means of the door wing may be taken into account or also not taken into account.

It is also particularly advantageous if the guide carriages / guide slides associated with a door wing are arranged along a spiral or propeller or are rotated in opposite directions about a horizontal axis and running parallel to the longitudinal extension of the longitudinal beam, where the end of a guide carriage / guide slide located farthest from the door wing, directed to the door leaf is lowered against a guide carriage / guide slide located closest to the relative door leaf to a course of the longitudinal beam. In other words, the guide carriages / guide slides are in turn rotated in opposite directions more intensively than would be necessary for tension-free guidance on the longitudinal beam (rotated), although now with respect to an axis running in parallel to the longitudinal extension of the longitudinal beam. Therefore, the transverse beam is prestressed after mounting the system on the longitudinal beam, and specifically so that it rotates the two guide carriages / guide slide opposite to the rotation of the longitudinal beam. The load is therefore reduced again by the weight of the door leaf on the guide carriage closest to the door leaf. Consequently the load between the guide carriages / guide slides can be precisely distributed. The aforementioned pre-stress may in turn be relative to both the unloaded longitudinal beam and the loaded longitudinal beam. Furthermore, a deformation of the cross beam may be taken into account or also not taken into account.

It is further advantageous if the guide carriages / guide slides associated with a door leaf are of different lengths and a guide carriage / guide slide closer to the door leaf is longer than a guide carriage / guide slide situated farthest from the door leaf. As already mentioned above, the guide carriage / guide slide associated with the nearest door leaf in an arrangement in which the door leaf, viewed in the longitudinal direction of the support / insert direction, is held in Cantilever in the crossbeam, as a general rule has to bear a much higher load than the guide carriage / guide slide located farthest from the door wing. It is now advantageous if a guide carriage / guide slide closer to the door wing is longer than a guide carriage / guide slide located farther from the door wing, so that the total load is well distributed in the guide carriages / individual guide slides. In particular, a load relative to the length of the guide carriage / guide slide closest to the door leaf and of the guide carriage / guide slide located furthest from the door leaf may be equal to or approximately the same. In other words, this means that the guide length for each support section near the door leaf is greater than the farthest from it. In other words, in that half of the total guide length that is closest to the door leaf, there is more support surface than in the most remote half.

It is further advantageous if the sliding door module / pivot and sliding door module has at least three guide carriages / guide slides associated with a door leaf and the average distance of the carriages of guide / guide slides with respect to the door wing is less than the average distance of the external guide carriages / guide slides with respect to the door wing. Similar to the example mentioned above, the total load is thus well distributed on the individual guide carriages / guide slides. Also in this case the guide length for each support section near the door wing is greater than the farthest from it. In other words, this in turn means that in that half of the total guide length that is closest to the door wing, there is more support surface than in the most remote half. Advantageously in this variant guide carriages / guide slides of equal length are used.

The measures mentioned according to which

- a guide / guide slide carriage located closer to the door wing is hingedly connected to the cross beam, while a guide / guide slide carriage located further from the door wing is rigidly connected to the cross beam ,

- a guide carriage / guide slide located closer to the door wing is longer than a guide carriage / guide slide located further from the door wing and

- more guide carriages / guide slides are arranged in a section located closer to the door leaf than in a section located further from the door leaf

they can be applied individually or in a discretionary combination. Especially advantageous is when all three measures are combined.

It is also advantageous if the maximum static bending of the support with respect to its bearing points in the case of a door opening (slightly) open in the area of the door opening LW from 800 mm to 2300 mm is at least

millimeters for every kilogram of door swing weight.

Compared to the sliding door modules / pivoting and sliding door modules known from the state of the art, said sliding door module / pivoting and sliding door module presents a comparatively strong deformation. The sliding door / swing door module support is therefore precisely "soft" designed so that it essentially acts as a leaf spring and thus the transmission of shocks acting on the vehicle on Rails to the sliding door module / pivot and sliding door module are smoothed. As the linear guide does not hardly act on the guide, it has a useful life. The reduced weight of the bracket improves not only the energy efficiency of the rail vehicle but also the resonant frequency of the sliding door module / sliding door module in the direction of higher frequencies, so that vibrations with remarkable amplitude they cannot be excited or only to a small extent.

The maximum static deflection is measured in this respect with the vehicle on rails stationary and appears in a certain position of the support in a certain position of the door wing or of the door wings. Usually the strongest bending of the bracket appears in the case of a double swing sliding door in the center of the bracket with slightly swinging door wings (a large gap) and in the case of a swinging sliding door in the center of the bracket in the case of a semi-open sliding door and it can be determined exactly, for example in a computer simulation or a test.

The "door opening" designates the width of the passage when the sliding door is fully open and is measured as a function of the width with which the door wing or doors are opened, between the door frame, the door frame and a door wing or between the two door wings.

The deflection is indicated with respect to the weight of the door leaf or of the door leafs. To obtain the absolute bending, the value indicated in each case must be multiplied with the total weight of the door wings. If the weight of a door swing is, for example, 32.5 kg and it is a double swing sliding door with a span of 1600 mm, then a maximum absolute static bending of the support of at least

It is also favorable when the maximum static bending of the support with respect to its support points, in the case of an open door leaf in the area of the LW door opening from 800 mm to 2300 mm is at least

millimeters for every kilogram of door swing weight.

It is also favorable when the maximum static bending of the support between the external contact points of the guide carriages / guide slides that support the door wing with the profiled rail (i.e. in the total guide length) in the case of a door swing door width is additionally or alternatively at least 0.0075 mm, but in particular also 0.015 mm, 0.030 mm or even 0.075 mm for each kg of door swing weight. If the linear guide is a linear roller guide, then the maximum static bending of the support can also be relative to the contact points of the external rolling bodies that the door wing supports with the profiled rail. Also in this case the absolute bending can be obtained by multiplying the indicated value with the total weight of the door wings.

It is further favorable if the support is housed essentially with respect to its longitudinal extension at its end points. In this way a comparatively good damping effect of jerks acting on the vehicle on rails can be achieved. Furthermore, in this arrangement an advantageous mounting situation generally occurs.

However, it is also especially favorable if the support is housed with respect to its longitudinal extension essentially at Bessel points. Therefore, the weight of the support can be reduced with the same damping effect. Bessel points are advantageous positions of the supports of a loaded support and are approximately 22% of the length of the support. Its specific position, however, depends on the design of the support and the components mounted on it, as well as the weight distribution.

It is especially favorable also, when one of the support points of the support is configured as a fixed bearing and the other support point or the other support points is / are configured as a free bearing. In this way, a variation in the length of the support conditioned, for example, by temperature or a variation in the distance between the end points of the support in the event of a flexion of the latter, can be compensated.

It is advantageous if the support in cross section on both sides of the profile rail is higher than in the area of the profile rail. In particular, for this purpose, the support in cross section on its upper and lower side on the sides of the profiled rail has an elevation. In particular, the support can also have an essentially H-shaped or X-shaped or T-shaped cross section. Therefore, on the one hand, the vertical flexural strength can be increased, on the other hand, the flexural resistance can also be increased. horizontal of the support with the same weight or its weight reduced with the same flexural strength. The support can therefore be designed in conjunction with relatively thin walls, whereby the total weight of the sliding door module / pivot and sliding door module is further reduced and thereby improve the running performance of the vehicle on rails. In addition to the improvement of the sliding door module / pivot and sliding door module in terms of vertical forces, it also causes an increase in resistance to bending in the horizontal direction or an increase in torsional stiffness around the longitudinal axis of the support .

It is also favorable if the support in the region of the neutral flexing fiber has a cavity, that is, the neutral fiber is arranged in the mentioned cavity. Therefore, the support has a relatively low weight, with good stability.

Especially advantageous is when the guide system comprises two linear guides, where a first profiled rail is mounted on the upper side of the support and a second profiled rail is mounted on the lower side of the support. In this way a single bracket can be used to hold a double-swing sliding and pivoting door. A sliding door / pivot and slide door module accordingly comprises a first pivot and slide door secured in the lower linear guide and a second pivot and slide door secured in the upper linear guide. The constructive height of the guide system in this arrangement is especially small. In particular it is also advantageous if the support is constructed symmetrical with respect to its horizontal axis, since then no special mounting direction has to be paid attention to.

It is advantageous if the profiled rail has an essentially C-shaped or U-shaped cross section and the guide carriage / guide slide is housed between the facing end branches of the C-shaped or U-shaped cross section Such a linear roller guide is hardly prone to unwanted stresses, so it is in use in the presented sliding door module / pivot and sliding door module has a comparatively long service life.

It is also particularly advantageous in the above context if the rolling bodies are arranged between an end branch of the profiled rail and the guide carriage / guide slide in a single row. For this reason, the linear guide is particularly tolerant against deformations of the guide system and is therefore particularly suitable for use in the case of rail vehicles. For the aforementioned reasons, the linear guide is also very durable.

It is especially advantageous if a drive for the door leaf is dimensioned in such a way that the flexing of the support during closing of the door leaf is reduced. A door wing suspended outwards due to bending of the support moves during closing towards the door frame or other sliding door and is oriented in the event of a further effect of the dimensioned drive with sufficient force. By means of the point of contact of the door leaf with the door frame or another door leaf, and the acting driving force acting on it actually acts a torque on it. Therefore, however, the support in its center is also pressed upwards, so that the flexion is reduced. By means of this tension, not only the bending of the support is reduced, but also the vibratory behavior of the sliding door module / pivot and sliding door module is modified, that is, it is displaced in the direction of higher resonance frequencies. Thus it can be said that the vibratory behavior of the sliding door module / pivot and sliding door module can be controlled by the drive for the door wings. As a drive, all kinds of rotary motors or linear motors come into question, for example electric, pneumatic and hydraulic drives. In particular, the supporting construction for a door leaf can be moved, for example, with the help of a spindle or a drive cable along the support.

Finally, it is also favorable if the door leaf is housed rotatably about an axis that runs in the longitudinal direction of the support. Therefore, on the one hand, tolerances can be compensated, on the other hand a sliding door module / pivot and sliding door module of this type can also be suitably integrated into vehicles on rails whose side walls are inclined. Rotation can be made possible, for example by clamping the door wing with the help of a bolt rotatably housed in the cross beam. But it is also conceivable that the door wing is fixedly connected to the cross beam, but that it is rotatably housed relative to the profiled rail.

For a better understanding of the invention this is explained in more detail by means of the following figures. Show

Figure 1 a sliding door module / pivot and sliding door module of a vehicle on rails by way of example very simplified and represented with exaggerated deformation;

2 shows the support and the guide carriages of the sliding door module / sliding and pivoting door module in isolated representation;

Figure 3 a sliding door / sliding door module support with two guide carriages of different length;

Figure 4 a sliding door module / sliding door module holder with three guide carriages with the same length, but unevenly distributed

Figure 5 as Figure 1, only with closed door wings and therefore less deformation of the sliding door module / pivoting and sliding door module;

Figure 6 a sliding door module / sliding and pivoting door module, in which a transverse beam joining two guide carriages is hingedly connected therewith;

Fig. 7 a sliding door module / sliding and pivoting door module in which the guide carriages are oriented on the cross beam without load according to a course of the longitudinal beam in the loaded operating state;

Figure 8 as Figure 5 or 6, but with a guide carriage fixedly attached and a guide carriage hingedly attached to the cross beam;

Figure 9 as Figure 8, but without door swing and with a hinged joint lowered with respect to a rigid connection between cross beam and guide carriage;

Figure 10 similar to Figure 7, although with guide carriages, which are rotated in opposite directions with respect to the course of the longitudinal beam about a horizontal axis transversely to the longitudinal beam;

Figure 11 similarly to Figure 9, but also with guide carriages rotated in opposite directions;

Figure 12 an exemplary sliding door / pivot door module with sliding drawings drawn;

Figure 13 a cross section through the sliding door module / pivot and sliding door module of figure 12 at the height of the front (right) guide carriage;

Figure 14 a cross section through the sliding door module / pivot and sliding door module of figure 13 at the height of the rear guide carriage (left);

Figure 15 similar to Figure 13, although without a door or longitudinal beam;

Figure 16 is similar to Figure 14, but without a longitudinal beam and with a rear guide carriage that is rotated about an axis oriented along the longitudinal beam with respect to the front guide carriage;

Fig. 17 an exemplary and schematically illustrated guide system for a sliding door module / pivot and sliding door module in tilted view;

Figure 18 the guide system of figure 17 in cross section;

Figure 19 the guide system of figure 17 in longitudinal section;

Figure 20 as Figure 19, only with an elastic element between bracket and counter support;

FIG. 21 shows a joint with generally cylindrical running surfaces with transversal axes to each other; Figure 22 an articulation with curved running surfaces of various dimensions and

Figure 23 a guide system with guide carriage arranged vertically.

As an introduction, it can be established that in the differently described embodiments the same parts are provided with the same reference numbers or the same designations of construction parts, the disclosures contained in the entire description being able to be transferred according to the meaning to the same parts with the same reference numbers or designations of construction parts. Also the data on selected positions in the description, such as above, below, laterally, etc., refer to the figure directly described and represented, and in the case of a variation of position according to the sense, they must be transferred to the new position . Furthermore, individual characteristics or combinations of characteristics from the different exemplary embodiments shown and described can individually represent autonomous solutions, inventive or according to the invention.

All data regarding ranges of values in the specific description are to be understood so that they comprise discretionary subintervals and all subintervals therefrom, for example data 1 to 10 are to be understood so that all subintervals are comprised, starting from the lower limit 1 and the upper limit 10, that is, all the sub-intervals start with a lower limit of 1 or greater and end in an upper limit of 10 or less, for example 1 to 1.7, or 3.2 to 8 , 1 or 5.5 to 10.

For better orientation in the figures, an x-y-z coordinate system is also drawn.

Figure 1 shows sliding door module / pivot and sliding door module 1 for a vehicle on rails in very simplified representation. The sliding door module / pivoting and sliding door module 1 comprises two door hinges 2 and a support 3 oriented longitudinally in the direction of insertion of the door hinges 2, which in the case of a pivoting and sliding door module can move transversely to its longitudinal extension in the horizontal direction, or in the case of a sliding door module it is fixedly housed. In addition, the sliding door module / sliding and pivoting door module 1 it comprises a linear guide, which in this example is made specifically as a linear roller guide. The linear roller guide comprises a profiled rail and two guide carriages 4, the profiled rail being attached to or supported by the support 3 in the form of a profiled area. In Figure 1, the profiled rail for a better overview is not explicitly represented (for details, however, see Figures 17 and 18). For the following reflections it can therefore be understood as understood by the support 3.

In the example shown, each door wing 2 is associated with two guide carriages 4 in each case. For this, they are connected to each other through a transverse beam 5 rigidly. The door wing 2 is fastened through a bracket 6 on the cross beam 6. In the example shown in figure 1, a first profiled rail is fastened on the upper side of the support 3 that is associated with the right door wing 2. A second profiled rail mounted on the underside of bracket 3 is associated with left door wing 2.

The support 3 in the concrete example is housed with respect to its longitudinal extension essentially at its end points. In this regard, the support point of the left support 3 is configured as a fixed bearing 7 and the right support point as a free bearing 8. With the two bearings 7 and 8 the support 3 is housed in a vehicle on rails (not shown).

As shown in figure 1 (exaggeratedly), the support 3 due to the weight of the sliding door module / pivot and sliding door module 1 flexes downwards, so that the two door wings 2 swing outwards. The maximum static deflection y1 of the support 3 in the case of an open door leaf 2 with respect to its bearing points 7, 8 in the area of the door opening LW is 800 mm to 2300 mm, advantageously at least

millimeters for every kilogram of door swing weight. Since the support 3 at its ends is housed in the bearings 7 and 8, the maximum static flex y1 appears in the center of the support 3, especially when the door is opened with a wide gap. However, depending on the housing of the support 3, the maximum static bending y1 may also appear elsewhere on the support 3. The absolute bending can be obtained using the span in the formula and by multiplying the indicated value with the total weight of the door wings. .

Additionally or as an alternative to this, the maximum flexion y2 of the support 3 between the contact points of the external rolling bodies, which support a door wing 2 with the profiled rail when the sliding door is open, can be at least 0.0075 mm , in particular at least 0.015 mm, 0.030 mm or 0.075 mm per kg of door swing weight. The absolute bending can be obtained in each case by multiplying the indicated value with the total weight of the door wings.

Figure 2 shows for this a more simplified representation. In this regard, only the guide carriages 4 of the right-hand door wing 2 on the support 3, or of the profiled rail, are shown. The guide carriages 4 are housed on the profiled rail by means of rotating rolling bodies 9. By means of the door wing 2 moment M is applied to the support structure, whereby the lower left ball of the left linear guide 4 and the upper right ball of the right linear guide 4 are subjected to comparatively high load. These two balls 9 are represented black in each case and with the profiled rail they form the external contact points 10 and 11. By these two points 10 and 11 the total guide length g is defined, over which the flexure y2 is measured. The two linear guides 4 each have the guide length f. From figure 2 it also follows that the guide lengths f of the guide carriages 4 in sum (i.e. in this case 2f) are less than the distance from the mentioned contact points 10 and 11, i.e. less the length total guide g. This tends to a tension of the linear guide. It should be noted in figure 2 that the flexion y2 corresponds purely accidentally to half the length of the support 3. This is naturally not a mandatory condition and the flexion y2 can also be less or greater than half the length of the support 3.

In reality, support 3 not only shows bends in the vertical direction but also in the horizontal direction. This is because pressure swings act on the door wings 2 and in this way they can bend the support 3 also in the horizontal direction. Consequently, there is also a normal bending moment at moment M shown in FIG. 2 and therefore a moment overlap. The values indicated for the flexion, however, refer to the stopped vehicle without the influence of pressure oscillations, so that the relevant moment M for this is caused (only) by the weight.

Compared to the sliding door modules / pivot and sliding door modules known from the state of the art, the sliding door module / pivoting and sliding door module 1 shown in Figures 1 and 2 has comparatively strong static flexion. The carrier 3 is therefore precisely "soft" designed so that it essentially acts as a leaf spring and thus smooth the transmission of shocks acting on the vehicle on rails towards the sliding door module / sliding and pivoting door module 1. Due to the reduced weight of the bracket 3 also the resonant frequency of the sliding door module / pivoting and sliding door module 1 is It shifts in the direction of higher frequencies, so vibrations with remarkable amplitude or only small dimensions cannot be induced.

To further reduce the weight of the support 3 with the same flex y1, y2, provision can also be made for the support points to move somewhat inwards. In FIG. 2, for this, the alternative support points 12 and 13 are shown, shifted the length a inwards. Preferably the support points 12 and 13 are arranged at the Bessel points, for which a = 0.22. In this arrangement, not only the reduced weight but also the reduced free vibration length of the support 3 is advantageous, since vibration knots are necessarily present at the support points 7, 8, 12 and 13. The resonant vibration of the sliding door module / sliding and pivoting door module is thereby further displaced in the direction of higher frequencies (and possibly also lower amplitudes).

In Figure 2 the two guide carriages 4 run only on a profiled rail. It would also be conceivable that these are guided on two profiled rails spaced from each other. However, also in said arrangement the total guide length g may be provided, that is to say the two guide carriages 4 may be spaced from each other in the insertion direction. If the profile rails are arranged one behind the other then Figure 2 can be understood directly as a projection of said arrangement in the plane of the sheet or front view (the rear guide carriage 4 should then be shown hidden by the profiled rail located in front).

Figure 3 shows an alternative embodiment example, in which two guide carriages 4 of different length are provided. Specifically, the right guide carriage 4 (that is to say located closer to the door wing 2) is configured longer than the left guide carriage 4 (that is to say located further from the door wing 2). Thus it can be avoided that the right guide carriage 4 with more load wears out earlier and has to be changed or maintained than the left guide carriage 4. In a corresponding design it can be achieved that the two guide carriages 4 wear almost the same and can be changed together. For a very similar reason, more than two guide carriages 4 can also be provided, which are unevenly distributed along the support 3 or cross beam 5.

FIG. 4 shows for this purpose an example with three guide carriages 4 with the same length, whose average distance from the door wing 2 is less than the average distance from the two external guide carriages 4 with respect to the door wing 2. Similar to the example mentioned above in this way the total load is suitably distributed on the individual guide carriages 4. Also in this case the guide length f for each support section near the door wing 2 is greater than when it is away from it. In other words, this in turn means that in that half of the total guide length g, which is located closer to the door wing 2, more support surface (or balls 9 are present) than in the half located more. away. Advantageously, in this variant as shown, guide carriages 4 with the same length are used. However this is not a mandatory condition. The guide carriages 4 can also be of different lengths, as shown in figure 3.

In general, a tension of the linear guide can be avoided when using tolerant guide systems. For example, single-row guide systems (i.e. with a row of balls) with a C-shaped or U-shaped profile (see also Figures 17 and 18) are generally comparatively resistant to stress and can be used thus suitably for a sliding door module / pivot and sliding door module 1. In a very general way, several (in particular two) guide carriages 4 can also be provided, which are in contact with each other, as shown by way of example in figure 4. Advantageously the guide carriages 4 can be tilted towards each other and thus adequately follow a flexing of the support 3. However these arrangements remain compact in external dimensions.

In an advantageous variant of the sliding door module / sliding and pivoting door module 1 an actuation for the door wings 2 is dimensioned such that the flexure y1, y2 of the bracket 3 is reduced during the closing of the door wings 2 Figure 5 shows the arrangement of Figure 1 with the doors closed. The outwardly suspended door wings 2 move in this respect through the mentioned drive (not shown) towards each other until they are in contact with each other in the lower area. If the drive is dimensioned with sufficient intensity then, a further movement produces a straightening of the door wings 2, since on these due to the driving force acting in the area of the support 3 and its contact point in the lower area a twisting moment acts. However, therefore also the support 3 is pressed upwards in the center, so that the flexure y1, y2 is reduced. Finally, with this, also the vibratory behavior of the sliding door module / pivoting and sliding door module 1 is improved, that is, it is displaced in the direction of higher resonance frequencies. In this regard, it is also important that the door wings 2, due to the lever effect, press against each other with a high force and, as regards vibratory behavior, they act as a single door wing 2 with double mass and therefore frequency. low resonance. In the case of a sliding door of a hinged, the door hinged 1 is pressed against the wagon wall of less or greater rigidity, so that vibrations can also be induced only to a small extent.

It can therefore be said that the vibratory behavior of the sliding door module / pivot and sliding door module 1 can be controlled by the drive. All types of rotary or linear motors, for example electric, pneumatic and hydraulic drives, are considered as drives. In particular, the supporting construction 4, 5, 6 for a door leaf 2 can be moved along the support 3, for example, with the aid of a spindle, a drive cable or a rack drive.

FIG. 6 now shows a further exemplary embodiment variant of a sliding door module / sliding and pivoting door module 1, in which the guide carriages 4 are hingedly connected with the cross beam 5 or with the hinged door 2. Symbolically, for this purpose, in FIG. 6, a rotating bearing 14 is shown on both guide carriages 4. Furthermore, FIG. 6 shows that a fixed bearing and a free bearing do not necessarily have to be provided for housing the support 3 In its place, two fixed bearings can also be provided at the support points 7 and 8. Finally, figure 6 also shows that a sliding door module / pivoting and sliding door module 1 does not have to be made by force with two hinges. , but can also comprise only a door leaf 2.

Due to the two rotary bearings 14, the two guide carriages 4 can suitably follow the course of the support 3 or the profiled rail mounted on it. However, it would also be conceivable to mount the guide carriages 4 on the unloaded cross beam 5, so that they are oriented along a course of the longitudinal beam 3 in the loaded operating state. Figure 7 shows for this purpose an example in which this principle is clarified. The transverse beam 5 in the state shown in FIG. 7 is not subjected to a load, which is also symbolically expressed because no door wing 2 is mounted on it. Additionally, also the course of the longitudinal beam 3 in the operating state with load (that is, when in particular a door wing 2 is also mounted) is represented in the form of an arc line or bending line drawn with dashed and dotted lines. The guide carriages 4 are now mounted rotated in opposite directions on the cross beam 5 which are oriented along the aforementioned arc line. In the state of the support 3 without load the two guide carriages 4 in opposite directions, which nevertheless continues without being detrimental because these in this state do not move or only a little on the profiled rail. If the door leaf 2 is mounted and the support 3 consequently enters the loaded operating state, then however there is hardly any tension present in the guide carriages 4. The use of rotary bearings 14 can therefore be omitted.

Only two guide carriages 4 are shown in FIG. 7. Naturally, however, the principle presented can also be extended to more than two guide carriages 4, which are then oriented accordingly on the aforementioned arc line. Furthermore, it is established that the cross beam 5 under load is also deformed and bends somewhat upwards, whereby the effective rotation of the guide carriages 4 is somewhat reduced. Consequently, the rotation of the guide carriages 4 about the unloaded transverse beam 5 in front of figure 7 may be somewhat more intense or the arc may run more pronounced.

In general, the rotation of the guide carriages 4 can for example be caused because wedges are inserted between the cross beam 5 and the guide carriages 4, or because the corresponding mounting surfaces are milled or chamfered.

In FIG. 7 reference was made by way of example to an arc-shaped bending line. It would naturally also be conceivable that the support 3 be deformed in another way and show, for example, an S-shaped bending line. This case appears, for example, then when the support points of the support 3 are in relation to their ends, as represented in figure 2 for the support points 12 and 13. Therefore also a bending line with another shape in general can serve as a basis for the measurements according to the invention.

Figure 8 now shows a variant of a sliding door module / sliding and pivoting door module 1, in which the guide carriage 4 located closest to the door wing 2 (i.e. in this case the right) is attached in an articulated manner and the guide carriage 4 located furthest from the door wing 2 (that is, in this case the left) is rigidly connected to the crossbeam 5. In this way, the right guide carriage 4 practically does not absorb moments of torsion about a horizontal axis of rotation transverse to its longitudinal axis (that is, around an axis of rotation located perpendicular to the plane of the blade or the y-axis). In contrast to this, the left guide carriage 4 can absorb said torque. In this way the total load can be properly distributed on the individual guide carriages 4.

In figure 6 the right guide carriage 4 due to the cantilever suspension of the door leaf 2 is clearly more loaded than the left guide carriage 4. By means of the arrangement shown in FIG. 8, however, some of the load from the right guide carriage 4 can now be moved to the left guide carriage 4.

For this purpose, it can also be provided that the articulated connection 14 (on the right) is recessed against the rigid connection (on the left) with respect to the course of the longitudinal beam 3, as shown in FIG. 9 in the example of the support 3 without load and with it essentially running in a straight line. The transverse beam 5 in the case of loading is then forcibly at the point of the pivotally housed guide carriage 4 tilts somewhat downward, or is therefore deformed by loading whereby the rigidly housed guide carriage 4 is loaded with a torque. The further the housed guide carriage 4 is lowered, the more the rigidly housed guide carriage 4 is loaded. In this way the load can be transmitted very precisely from the right guide carriage 4 to the left guide carriage 4. In this regard, the spring constant of the cross beam 5 which acts at the same time as a leaf spring housed on one side .

In figure 9 the principle presented for the sake of a better representation is represented in the support 3 without load and straight. In a particularly advantageous variant of the sliding door module / pivot and sliding door module 2 the mentioned recess is with respect to the course of the longitudinal beam 3 in the loaded operating state, that is to say to a state in which the wing (s) of door 2 are mounted. By the resulting bending of the longitudinal beam 3 (see also FIG. 8) the recess of the articulated housed guide carriage 4 may become somewhat more intense before a torque is applied to the rigidly housed guide carriage 4 noteworthy transversely to its longitudinal axis (i.e. around the y-axis).

In this model the longitudinal beam 3 for the provision of the mentioned recess although it is subjected to load and therefore deforms, however the transverse beam 5 is assumed to be without load. In principle, the course of the support 3 would therefore correspond accordingly to the course shown in FIG. 8. From FIG. 9 it is clarified that the recess provided therein for the guide carriage 4 housed in an articulated manner in the case of a support 3 deformed according to FIG. 8 is not sufficient to cause a clockwise torque on the left guide carriage 4. In order to generate said torque, the recess, therefore, as already mentioned, should be greater so that also in the case of a deformed support 3 according to FIG. 8, there is still a play in the rotary bearing 14. Until also the cross beam 5 is assumed to be loaded the cross beam 5 does not come into contact with the rotary bearing 14 and then causes the desired torque. In reality, a deformation of the support 3 according to FIG. 8 is naturally only possible when the crossbeam 5 is also subjected to load and is deformed.

In the above cases it was assumed that the torque caused on the left guide carriage 4 is oriented clockwise. This is advantageous but not absolutely necessary. It may also be provided that the torque is oriented differently counterclockwise.

The mentioned recess can be carried out in various ways, for example by providing a corresponding bearing set that disappears with load. In Figures 19 to 21 the distance between transverse beam 5 and counter bearing 20 could therefore be greater than that shown. In principle, the provision of a play may also not take place if, for example, the cross beam 5 is pre-tensioned. In Figures 19 to 21 in the case of an unloaded transverse beam 5 there is therefore a distance between the transverse beam 5 and the counter bearing 20 which disappears in the assembly of the sliding door module / pivot and sliding door module 1 by tightening the screws 22. The cross beam 5 is then bent down correspondingly and the left guide carriage 4 in figure 9 forces a torque clockwise. On the contrary, the right guide carriage 4 is pulled upwards. When mounting the door leaf 2, its weight is superimposed on the aforementioned pre-tension. The load on both guide carriages 4 can thus be controlled within wide limits.

Figure 10 shows a variant of a sliding door module / pivot and sliding door module 1, in which the guide carriages 4 associated with a door wing 2 similar to figure 7 are arranged along a arc or are rotated in opposite directions about a horizontal axis and running transversely to the longitudinal extent of longitudinal beam 3 (i.e. about the y-axis). Additionally, however, also the end directed to the door wing 2 of the guide carriage 4 located furthest from the door wing 2 (that is, the right end of the left guide carriage 4 in Figure 10) compared to the guide carriage 4 located closest to the door wing 2 (ie the right guide carriage 4 in Figure 10) with respect to a course of the longitudinal beam 3. However, the arrangement can also be understood such that the end opposite the door leaf 2 of the guide carriage 4 located closest to the door wing 2 (i.e. the left end of the right guide carriage 4 in Figure 10) is lowered in front of the guide carriage 4 (i.e. the left guide carriage 4 in Figure 10) located furthest from the door wing 2 with respect to a course of the longitudinal beam 3. A concept is also possible according to which both ends directed towards each other of the guide carriages 4 are lowered. words, the chariots of g Guide 4 are rotated in opposite directions more intensively than would be necessary for tension-free guidance on longitudinal beam 3 (flexed). Therefore, the transverse beam 5 after mounting the arrangement on the longitudinal beam 3 is flexed upward and prestressed, whereby the guide carriages 4 are dragged upwards by the transverse beam 5. Hence the load through The weight of door leaf 2 is reduced on the right guide carriage.

In figure 11 the principle shown in figure 10 has been applied in the arrangement already shown in figure 9. Due to the rotary bearing 14 in the right guide carriage 4 no torque can be transmitted to the some or none notable, so its load is comparatively reduced. In this representation the pre-tension refers to the support 3 without load, which would also be possible in the arrangement shown in figure 10 possible. Naturally the pre-stress can also refer to the course of the longitudinal beam 3 in the loaded operating state. It is of course generally conceivable also that the longitudinal beam 3 is prestressed flexed upwards.

Figures 12 to 16 show a further variant of a sliding door module / pivot and sliding door module 1, in which a rotation of the longitudinal beam 3 is contemplated. Figure 12 shows in this regard an arrangement with the sectioned guide for Figures 13 to 16.

Figure 13 shows a cross section AA through the sliding door module / pivot door module and sliding door 1 at the height of the n (4) front guide carriage (right). Fig. 14 shows a cross section BB through the sliding door module / pivot door module and sliding door 1 at the height of the rear guide carriage 4 (left). As can be distinguished from figure 13, the weight of the door wing 2 causes a torque that acts on the longitudinal beam 3 in the counterclockwise direction.

In Figures 13 and 14 the guide carriages 4 are not rotated in opposite directions. This is different in the arrangement shown in Figures 15 and 16, in which the guide carriages / guide slides 4 associated with a door wing 2 are arranged along a spiral or helix or are rotated in opposite directions around of a horizontal axis and which runs parallel to the longitudinal extension of longitudinal beam 3 (that is to say around the x-axis). In this regard, the end directed to the door wing 2 of the guide carriage 4 located furthest from the door wing 2 l (that is to say in this case the left end of the guide carriage 4 shown in Figure 16) is lowered compared to a Guide carriage 4 located closest to door wing 2 with respect to a course of longitudinal beam 3 (compare Figure 15). In other words, the guide carriages 4 are rotated in opposite directions more intensively than would be necessary for tension-free guiding on the longitudinal beam 3 (rotated). For this reason, after mounting the arrangement on the longitudinal beam 3, the transverse beam 5 is rotated in the opposite direction to the posterior rotation of the longitudinal beam 3 and is therefore pre-tensioned. In particular, the pre-tension is selected such that the bracket 6 after mounting the door leaf 2 is oriented essentially parallel to the support 3.

Due to the rotary bearing 14 in the guide carriage 4 of figure 15 (and also in the guide carriage 4 of figure 13), no or any remarkable torque can be transmitted, so that its load is comparatively low. The torque caused by the door wing 2 through the bracket 6 is therefore transmitted essentially from the left guide carriage (see also Figures 14 and 16).

In this representation the pre-tension refers to the support 3 without load. Naturally the pre-stress can also refer to the course of the longitudinal beam 3 in the loaded operating state. It is also generally conceivable of course that the longitudinal beam 3 is prestressed and rotated somewhat at the height of the cut BB in FIG. 16 clockwise. It is naturally conceivable in this variant embodiment also that the rotary bearing 14 is omitted (compare also Fig. 10 for the direction). It is further conceivable that the rotary bearing 14 acts only in one direction, that is to say it allows only one rotation around an axis parallel to the longitudinal direction of the support 3 (x-axis) or about a horizontal axis transverse to it (y-axis) ).

In this arrangement, it should be noted that the data for the distance of the guide carriage 4 from the door wing refers to FIG. 12 (that is, to the longitudinal direction of the support 3), while the data "the directed end" of the carriage guide 4 refers to figure 16 or figure 15 (ie to the transverse direction of the support 3).

In a similar way as explained in figure 7 regarding flexing of the support 3, the guide carriages 4 can be mounted on the transverse beam 5 without load so that they are oriented according to a course of the longitudinal beam 3 in the loaded operating state, specifically according to its rotation. In this regard it is again assumed that the cross beam 5 is not decisively deformed, or in any other way than the support 3. The guide carriages 4 are now mounted rotated in opposite directions on the cross beam 5 so that they are oriented along a spiral or helix. In the state of the support 3 not loaded, the two guide carriages 4 are tensioned in opposite directions, which, however, is still not harmful because these in this state do not move or only a little on the profiled rail. If the door leaf 2 is mounted and the support 3 consequently enters the loaded operating state, however, there is practically no longer any tension on the guide carriages 4. The use of rotary bearings 14 can therefore be omitted again.

The examples shown in Figures 8 to 16 comprise only two guide carriages 4 associated with the door leaf 2. Of course, the principle presented can also be extended to more than two guide carriages 4. In particular, a discretionary combination of measures is also possible represented in figures 3, 4 and 7 to 16. For example the guide carriages 4 can be rotated in opposite directions both about a horizontal axis (y-axis) and that runs transversely to the longitudinal extension of the longitudinal beam 3, as about an axis (x-axis) horizontal and running parallel to the longitudinal extension of the longitudinal beam 3. In this regard the guide carriages 4 can be oriented on the transverse beam 5 without load according to a course of the beam longitudinal 3 in the loaded operating state, so that during operation no noticeable additional stress appears on the crossbeam 5, or the crossbeam 5 is actively prestressed, as shown in Figures 9 to 11 as well as 15 and 16 In this respect, the door wing 2 by means of a guide carriage 4 located farthest from the door leaf 2 in the area of a guide carriage 4 located closest to the door leaf 2 rises somewhat. Furthermore also guide carriages 4 (FIG. 3) of different length or guide carriages 4 in the course of the support 3 differently distributed (FIG. 4) may be arranged / oriented rotated in opposite directions or along an arc and / or a spiral or helix. Furthermore, the use of rotary bearings 14 that allow a rotation about one or two axes is generally conceivable.

In a very general way, a deformation of the cross beam 5 can also be considered, as already explained in relation to FIG. 7. In most cases, the cross beam 5 will not deform in the same way as the support 3, it is say it will not bend or rotate like this. The rotation of the guide carriages 4 on the transverse beam 5 can then be correspondingly somewhat more intense or less intense than in the case of the rigidly assumed transverse beam 5.

Figures 17 and 18 now show an exemplary guiding system for a sliding door module / pivot and sliding door module in somewhat more detailed representation in diagonal view (Figure 17) as well as in diagonal section (Figure 18). The guide system comprises the support 3 as well as the linear roller guides with two profiled rails 15, which are fastened on the support 3 (for example screwed with it) or included by it in the form of a profiled area. The profile rail 15 in this example has an essentially C-shaped or U-shaped cross section, a guide carriage 4 being housed between the facing end branches of the C-shaped or U-shaped cross section. The use of this special guide rail 15 is not mandatory, and other types of linear roller guides can also be used.

Furthermore, the guide system comprises a transverse beam 6 with a bracket 6 fixedly attached to it, in which a mounting plate 16 for a door wing 2 is rotatably housed with the help of a bolt 17. The profiled rail 15 is in FIG. 17 it does not extend over the entire length of the support 3. Naturally this may however be the case. The support 3 is housed in a sliding manner transversely to its longitudinal extension in the horizontal direction, which in figure 17 is symbolized by the double arrows arranged laterally. In this regard, the support 3 is tilted outwards transversely to the direction of insertion of the door leaf so that the door leafs can move. In particular, in such a construction mode, attention must be paid to the reduced weight of the entire arrangement since it places a load on the support guide system 3 (not shown) in a comparatively intense way. However, the support 3 can also be fixedly connected to the vehicle on rails.

In figure 17 it can be clearly seen that in this example two linear guides are provided, a first profiled rail 15 being mounted on the upper side of the support 3 and a second profiled rail 15 on the lower side of the support 3. In this way it can be used a single support 3 to hold a double swing pivot and sliding door. In particular it is also advantageous when the support 3 is built symmetrically with respect to the horizontal plane, since then no attention has to be paid to any special mounting direction.

In Figure 17 it can also be seen suitably that the crossbeams 5 and brackets 6 of the lower and upper linear guide in this example are essentially identical and are guided 180 ° about a horizontal axis (y-axis) and oriented perpendicular to the profiled rail 15. For this reason, the number of different construction elements of the guide system is reduced and with this the manufacturing as well as the storage are simplified. As can be seen properly in particular from figure 18 the profiled rails 15 protrude from the support 3 in this example in the mounting area of the profiled rails 15 in the vertical direction. From figure 18 it can also be seen that in this embodiment an imaginary connection line of two rolling bodies 9, which are in contact with the profiled rail 15 and are arranged facing each other with respect to a gravity axis 18 of the cross section of profile oriented perpendicular to the mounting surface, it is essentially horizontally oriented. Furthermore, a plane of rotation of the rolling bodies 9 is oriented essentially horizontally. Furthermore, it can also be seen from FIG. 18 that an orbit 19 of the rolling bodies 9 is arranged on the guide carriage 4. Thus, the construction depth of the guide system can be kept small. Finally figure 18 also shows that the rolling bodies 9 are arranged between an end branch of the profiled rail 15 and the guide carriage 4 in a single row. For this reason, the linear guide is especially tolerant against deformations of the guide or support system 3 and therefore especially durable.

From figure 18 it can also be seen that the support 3 in the example represented in cross section on both sides of the profiled rails 15 is higher than in the area of the profiled rail 15. The support 3 presents in cross section for this purpose in its upper and lower side to the sides of the profiled rails 15 an elevation. In this example, the support 3 therefore has an essentially H-shaped or X-shaped or T-shaped cross section. Therefore, the flexural strength of the support 3 can be clearly increased on the one hand vertical and on the other hand also the horizontal. The support 3 can also be made hollow. In particular the cavity can be arranged in the neutral fiber of the support 3.

Figures 19 and 20 now show two detailed embodiment variants for a rotary bearing 14 (also see Figures 6, 8, 9, 11, 12, 13 and 15).

Figure 19 shows a section DD, from which it can be seen that the transverse beam 5 in the area of the guide carriage 4 has a convex section, which rests on the flat surface of the guide carriage 4 so that a rotary joint is formed or swivel bearing 14 with two running surfaces that roll towards each other. As the guide carriage 4 is generally made of highly resistant and tempered steel, the upper side of a commercially available guide carriage can act as a running surface without additional measures. Specifically, the running surface arranged on the cross beam 5 has a cylindrical shape, where the projecting ends are perpendicular to the sheet plane. The cross beam 5 and thus a door wing 2 attached to it can therefore be rotated about an essentially horizontal axis of rotation (y-axis) and oriented transversely to the direction of insertion with respect to the profiled rail 15, whereby vertical bending of the profile rail 15 can be compensated.

In this example, the two running surfaces are pressed against each other by a weight of the door leaf 2. Additionally, the two running surfaces that roll towards each other are protected from lifting with the help of an optional counter bearing 20. The counter bearing 20 is fixed in position with the help of alignment bolt 21 with respect to the cross beam 5 and with the help of screws 22 is screwed with it. However, in order to make possible a rotation of the transverse beam 5 with respect to the profiled rail 15, as shown in FIG. 19, the counter support 20 can be convex in shape and / or allow a reduced play. In the latter case a lifting of the running surfaces is therefore possible in principle, although the "drop height" (ie clearance) is selected so small that damage to the running surfaces can be avoided by colliding the cross beam 5 with guide carriage 4.

Figure 20 shows a variant of the guide system, which is very similar to the variant shown in figure 19. Unlike this the optional counter bearing 20 presses the running surfaces against each other with the help of a spring force and / or through elastic deformation. Specifically, the transverse beam 5 with the counter bearing 20 is screwed for this by means of two rubber stops 23 that allow a rolling of the running surfaces with a moderate energy expenditure, but prevent a lifting of the running surfaces or at least hinder . In the example shown in FIG. 20, the counter bearing 20 does not have a convex area, but it is naturally also conceivable that it is formed as shown in FIG. 19, whereby rolling of the running surfaces is facilitated.

In principle for the arrangement shown in figure 20 it is sufficient when the cross beam 5 can be moved in translation with respect to the counter bearing 20. However, in a variant of the arrangement shown in figure 20 the adjustment of the alignment bolt 20 can be selected also relatively loose or the alignment bolt can be housed in a rubber sleeve, so that the cross beam 5 and the counter bearing 20 are tilted towards each other. In a correspondingly loose fit, the counter bearing 20 can remain in this respect even even resting on the guide carriage 4 flatly when the crossbeam 5 tilts or rotates with respect to the guide carriage 4.

Although the joints shown in Figures 19 and 20 allow a rotation of the cross beam 5 with respect to the profiled rail 15 about an axis of rotation (y-axis) essentially horizontal and oriented transversely to the direction of insertion, the joints shown can provided by corresponding arrangement also for a rotation about a vertical axis of rotation (z-axis) or about an axis of rotation (x-axis) oriented essentially parallel to the insertion direction.

Figure 21 shows a highly schematic of a rotary joint 14 that enables a rotation about two axes of rotation (in the example shown around the y-axis and the z-axis). For this purpose, the transverse beam 5 and the optional counter bearing 20 have cylindrical running surfaces in general with axes perpendicular to each other. The guide carriage 4, on the other hand, again presents flat running surfaces. Such a rotary joint 14 can therefore compensate especially well for the deformations of a profile rail 15 or of the support 3. Due to the line-shaped contact of the running surfaces, comparatively high forces can also be transmitted. Of course the swivel joint 14 can also be used so that a rotation about other axes is allowed, for example around the x-axis and the y-axis or around the x-axis and the z-axis.

Figure 22 shows in a very schematic way a rotary joint 14 that makes possible a rotation about discretionary axes of rotation. For this purpose the cross beam 5 and the optional counter bearing 20 have curved running surfaces of various dimensions, in particular ball-shaped running surfaces. Said swivel joint 14 can compensate the deformations of a profiled rail 15 also in a particularly suitable way. Due to the curvature of various dimensions the running surfaces in case of a Rotation about a discretionary axis can roll towards each other, so sliding towards each other is avoided and the wear of the rolling surfaces is reduced thereby.

By providing a swivel joint 14 or several swivel joints 14, a deformation of the profile rail 15 is made possible without tensioning the housing between guide carriage 4 and profile rail 15. Opposite the sliding door modules / pivot and sliding door modules Known a support 3, on which the profiled rail 15 is attached, can therefore be designed comparatively fragile, since the door leaf 2, despite a deformation of the profiled rail 15, always continues to run smoothly and damage is avoided in the housing between guide carriage 4 and profiled rail 15. In addition, in a corresponding embodiment of the swivel joint 14 the provision of the bolt 17 is essential, that is, the rotation of the door leaf 2 about an axis (x-axis) running in the longitudinal direction of the support 3 can - at least in a certain angular range - also be assumed by the rotary joint 14. In figure 21 p A (additional) running surface can also be provided for this, which allows a rotation about the mentioned longitudinal axis (x-axis).

The articulated housings of the transverse beam 5 specifically shown in Figures 19 to 22 can be realized in particular then when the profiled rail 15 is housed only at its ends, so that the transverse beam 5 can comprise the guide carriage 4 together with the counter bearing 20 on all sides (see in particular Figures 21 and 22). If the profiled rail 15 as shown, for example, in Figure 17 is to be connected along its entire length with the support 3, then for example the counter support 20 may be omitted or the guide carriage 4 may have a corresponding extension, which instead it can be understood on all sides by the transverse beam 5 together with the counter support 20. In the arrangements shown in Figures 19 and 20 the mentioned extension can be arranged in particular on the sides on the guide carriage 4, in the arrangements shown in Figures 21 and 22 it can run in particular in the longitudinal direction.

In general, vertical flexions of the profiled rail 15 can be compensated by allowing a rotation of the bracket 6 with respect to the profiled rail 15 about an essentially horizontal axis of rotation (y-axis) and oriented transversely to the insertion direction, horizontal flexions when allowing a turn about an axis of rotation (z-axis) oriented essentially vertically and a torsion of the profiled rail 15 by allowing a rotation about an axis of rotation (x-axis) oriented essentially parallel to the insertion direction.

In general, turns can be made around several axes by means of individual pivot joints connected in series one behind the other (compare Figures 19 and 20) and / or by rotary joints that allow turns around several axes (compare Figures 21 and 22). . The swivel joints can optionally also be made by running surfaces that roll towards each other and / or surfaces that slide against each other (for example sliding bolt / sleeve). Furthermore, the positioning of the joints, as indicated in the previous examples, although advantageous, is not in any way mandatory. In principle, a swivel joint 14 can be provided on the guide carriage 4, between the cross beam 5 and the guide carriage 4, on the bracket 6, between the bracket 6 and the door leaf 2 and / or on the door leaf 2 itself. In the latter case, for example, a mounting surface for the door wings 2, on which the bracket 6 is attached, can be housed in an articulated manner around the door wing 2 itself.

Furthermore, it should also be noted that the use of compensating joints 14 is naturally not connected to a linear roller guide, although there a particularly fast tension of the housing can have a detrimental consequence. The invention can naturally be applied in the same way also on linear sliders of all kinds. Regarding figure 2, it should be noted that the maximum flexion y2 of the support 3 can also refer to the external points of the guide carriages / guide slides 4 that support a door wing 2. The guide length f, or the length total guide g is then measured outside on the guide carriages / guide slides 4 and not on the rolling bodies 9.

Finally, it should also be noted that the use of compensating joints 14 is naturally also not linked to the special arrangement of the profiled rails 15. Rather, the contact surfaces of the profiled rails 15 can be oriented vertically towards the support 3 as well. FIG. 23 shows for this purpose an example of a sliding door module / pivot and sliding door module 1, in which two door wings 2 are fastened through brackets 6 on the guide carriages / guide slides 4 of two linear guides arranged one on the other. The aforementioned teaching can be applied according to the meaning also to such an arrangement.

The exemplary embodiments show possible variants of embodiment of a sliding door module / pivot and sliding door module 1 according to the invention, wherein at this point it should be noted that the invention is not limited to the variant embodiments thereof Specially represented, but rather also various combinations of the individual embodiment variants are possible with each other and this possibility of variation due to the teaching for technical intervention by means of the specific invention resides in the knowledge of the expert in the field working in this field. technical. Therefore also all conceivable embodiment variants that are possible by the combinations of additional details of the embodiment variant represented and described are comprised by the scope of protection.

For example the guide carriages / guide slides 4 in the sliding door module / pivot and sliding door module 1 shown in figure 5 can also be rigidly connected to the cross beam 5. Likewise the guide carriages / guide slides 4 in the sliding door module / sliding and pivoting door module 1 shown in figure 1 can also be hingedly connected to the cross beam 5. The sliding door module / sliding and pivoting door module 1 shown in the figure 1 may furthermore have two fixed bearings, while the sliding door module / pivot and sliding door module 1 shown in FIG. 5 may also have a fixed bearing and a free bearing. Of course, the sliding door modules / pivot and sliding door modules 1 shown can have a guide carriage / guide slide 4 for each door leaf 2 or also two and more guide carriages / guide sliders 4 for each door leaf. 2.

In particular, it is established that a sliding door module / sliding door module 1 can in reality also comprise more or less components than those represented.

For the sake of order, it should finally be indicated that for the best understanding of the structure of the sliding door module / pivot and sliding door module 1, this or its components have not been partially represented in scale and / or have been represented with magnification and / or or decrease.

The independent inventive solutions on which the objective is based can be deduced from the description.

List of reference numbers

1 sliding door module / sliding and pivoting door module

2 door swing

3 support

4 guide carriage / guide slide

5 cross beam

6 bracket

7 support fulcrum

8 support fulcrum

9 rolling body

10 point of contact rolling body / profiled rail

11 contact point rolling body / profiled rail

12 fulcrum support

13 support fulcrum

14 swivel bearing

15 profile rail

16 mounting plate

17 bolt

18 axis of gravity

19 orbiting rolling bodies

20 counter support

21 alignment bolt

22 screw

23 rubber bumpers

separate part

f guide length

g total guide length

M torque

y1 maximum bending of the support (absolute)

y2 bending of the support between guide carriages / guide slides

Claims (23)

1. Sliding door module / pivoting and sliding door module (1) for a rail vehicle comprising: - at least one door leaf (2), - a support (3) oriented longitudinally in the direction of insertion of the door leaf (2), which is slidably housed in the horizontal direction, particularly transverse to its longitudinal extension, - a linear roller guide with at least one profiled rail (15), the at least one profiled rail (15) being attached to or supported by the support (3) in the form of a profiled area, and - at least two separate guide carriages / guide slides (4), in particular distanced from each other in the direction of insertion of the door leaf (2), which are associated only with a door leaf (2), with the which the door leaf (2) is slidably housed, characterized by that - the linear roller guide has several guide carriages / guide slides (4) with rotation of rolling bodies, where the guide carriages / guide slides (4) are housed on the at least one profiled rail (15), - the guide lengths (f) of the guide carriages / guide slides (4) are in sum at most half as long as the distance (g) of the external contact points (10, 11), which the guide carriages / guide slide (4) supporting the door wing (2) with the profiled rail (15), and - the guide carriages / guide slides (4) associated with a door wing (2) are connected - rigidly, - in an articulated way or - partially rigid, partially articulated with a transverse beam (5) that supports the door wing (2) or with the door wing (2). 2. Sliding door module / pivot and sliding door module (1) according to claim 1, characterized in that the guide carriages / guide slides (4) on the unloaded cross beam (5) are oriented according to a course of the longitudinal beam (3) in the loaded operating state. 3. Sliding door module / pivoting and sliding door module (1) according to claim 1 or 2, characterized in that a guide carriage / guide slide (4) associated with the door wing (2) and located close to it It is hingedly connected and a guide carriage / guide slide (4) associated with the door wing (2) located furthest from it is rigidly connected with the cross beam (5) or the door wing (2). 4. Sliding door module / pivoting and sliding door module (1) according to claim 3, characterized in that a hinged connection (14) is lowered with respect to a rigid connection with respect to the course of the longitudinal beam (3). Sliding door module / pivoting and sliding door module (1) according to one of Claims 1 to 4, characterized in that the guide carriages / guide slides (4) associated with a door leaf (2) are arranged along an arc or rotated in opposite directions about a horizontal (y) axis and that runs transversely to the longitudinal extension of the longitudinal beam (3), where the end is directed to the door wing (2) of a carriage guide / guide slide (4) located farthest from the door wing (2) is lowered in front of a guide / guide slide carriage (4) located closest to the door leaf (2) with respect to a course of the longitudinal beam (3). 6. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 5, characterized in that the guide carriages / guide slides (4) associated with a door leaf (2) are arranged along a spiral or helix or are rotated in opposite directions about an axis (x) horizontal and that runs parallel to the longitudinal extension of the longitudinal beam (3), where the end is directed to the door wing (2 ) of a guide carriage / guide slide (4) located furthest from the door wing (2) is lowered in front of a guide carriage / guide slide (4) located closest to the door leaf (2) with respect to to a course of the longitudinal beam (3). 7. Sliding door module / pivoting and sliding door module (1) according to one of claims 4 to 6, characterized in that the recess is relative to the course of the longitudinal beam (3) in the loaded operating state. 8. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 7, characterized in that the guide carriages / guide slides (4) associated with a door leaf (2) are of different length and a guide carriage / guide slide (4) closer to the door wing (2) is longer than a guide carriage / guide slide (4) located further from the door wing (2). 9. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 8, characterized in that it has at least three guide carriages / guide slides (4) associated with a door leaf ( 2) and the average distance of the guide carriages / guide slides (4) with respect to the door wing (2) is less than the average distance of the guide carriages / external guide slides (4) with respect to the wing. door (2). 10. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 9, characterized in that the maximum static flexion (y1) of the support (3) with respect to its bearing points (7, 8, 12, 13) in the case of an open door leaf (2) in the area of an LW door opening from 800 mm to 2300 mm is at least

millimeters for every kilogram of door swing weight. 11. Sliding door module / pivoting and sliding door module (1) according to claim 10, characterized in that the maximum static flexion (y2) of the support (3) between the external contact points (10, 11) of the carriages guide / guide slides (4) that supports the door wing (2) with the profiled rail (15) in the case of an open door wing (2) is at least 0.5 mm. 12. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 11, characterized in that the support (3) is housed with respect to its longitudinal extension essentially at its end points. 13. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 11, characterized in that the support (3) is housed with respect to its longitudinal extension at essentially Bessel points. 14. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 13, characterized in that one of the bearing points (7, 12) of the support (3) is configured as a fixed bearing and the other bearing point (8, 13) or the other bearing points is / are configured (8, 13) as a free bearing. 15. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 14, characterized in that the support (3) in cross section on both sides of the profiled rail (15) is higher than in the profiled rail area (15). 16. Sliding door module / pivoting and sliding door module (1) according to claim 15, characterized in that the support (3) in cross section on its upper and lower side on the sides of the profiled rail (15) has an elevation . 17. Sliding door module / pivoting and sliding door module (1) according to claim 15 or 16, characterized in that the support (3) has an essentially H-shaped or X-shaped or T-shaped cross section . Sliding door module / pivoting and sliding door module (1) according to one of Claims 1 to 17, characterized in that the support (3) in the region of the neutral flex fiber has a cavity. 19. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 18, characterized by two linear roller guides, where a first profiled rail (15) is mounted on the upper side of the support (3) and a second profiled rail (15) is mounted on the underside of the support (3). 20. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 19, characterized in that the profiled rail (15) has an essentially C-shaped or U-shaped cross section and the Guide carriage / guide slide (4) is housed between the facing end branches of the C-shaped or U-shaped cross section. 21. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 20, characterized in that the rolling bodies (9) are arranged between an end branch of the profiled rail (15) and the carriage guide (4) in a single row. 22. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 21, characterized in that a drive for the door leaf (2) is dimensioned in such a way that the flexing of the support (3) during the closing of the door leaf (2) is reduced. 23. Sliding door module / pivoting and sliding door module (1) according to one of claims 1 to 21, characterized in that the door leaf (2) is rotatably housed around an axis (x) running in the longitudinal direction of the support (3).