EP3059135A1 - Rail vehicle with a cooling facility - Google Patents

Abstract

The present invention relates to a cooling system (2) for a bidirectional rail vehicle (1), comprising at least one radiator (10), which extends transversely to a longitudinal direction (11), which in the installed state of the cooling system (2) parallel to the respective direction of travel (3, 4) of the vehicle (1), and horizontally by a cooling air flow (13) can be flowed through, and at least one inflow-side Strömungsleiteinrichtung (14) which is arranged on an air inlet side (15) of the radiator (10) and between a first switching position ( S1) in which, in a first direction of travel (3) of the rail vehicle (1), it deflects air from the longitudinal direction (11) in the transverse direction (12) to the air inlet side (15) and is adjustable to a second switching position (S2) in the case of a second direction of travel (4) of the rail vehicle (1), it deflects air from the longitudinal direction (11) in the transverse direction (12) onto the air inlet side (15). Increased efficiency results when the flow guiding device (14) extends in the longitudinal direction (11) over the entire air inlet side (15) of the respective radiator (10).

Description

The present invention relates to a cooling system for a bidirectional rail vehicle, having the features of the preamble of claim 1. The invention also relates to a rail vehicle equipped with at least one such cooling system.

A bidirectional rail vehicle is characterized in that it can travel in the two possible directions along the rails on which it is guided and drives.

From the DE 523 925 A a generic cooling system for such a bidirectional rail vehicle is known, which is designed as a roof construction cooling system. The cooling system has at least one radiator which can be traversed transversely to a longitudinal direction, which extends parallel to the respective direction of travel of the rail vehicle in the installed state, and horizontally by a cooling air flow. Furthermore, at least one inflow-side flow guide is provided, which is arranged on an air inlet side of the radiator and which is adjustable between a first switching position and a second switching position. In the first switching position, the flow guiding device deflects air from the longitudinal direction in the transverse direction to the air inlet side in a first direction of travel of the rail vehicle. In the second shift position, in a second direction of travel of the rail vehicle, which is opposite to the first direction of travel, the flow guiding device deflects air from the longitudinal direction in the transverse direction to the air inlet side. Thus, an efficient flow through the radiator is ensured with a cooling air flow for both directions of travel of the bidirectional rail vehicle.

In the known cooling system, the flow guide device comprises two groups of flow guide elements which each extend approximately over half of the air inlet side of the cooler and are adjustable between an open position and a closed position. In the open position, the flow guide elements of the respective group release a flow-through cross section assigned to this group, while blocking this cross section in a closed position. In the first switching position of the flow-guiding device, the flow-guiding elements of the first group preceding in the first direction of travel are moved into the open position, while the flow-guiding elements of the second group following in the first direction of travel are adjusted into their closed position. Accordingly, the cooling air flow can flow to the radiator only through the flow cross section of the first group. In the second switching position of the flow guide, however, the second group of the second direction of travel faces, while then the first group is arranged following it. Furthermore, it is provided in the second switching position that the flow guide elements of the second group are adjusted in their open position, while the flow guide elements of the first group are adjusted in their closed position. Thus, in the second switching position, the cooling air flow can only flow to the radiator through the flow cross section of the second group. The disadvantage here is that in both directions of travel of the rail vehicle, the cooling air flow is limited by the cross section of the first group or the second group, which is smaller than the cross-section through which the radiator can flow.

From the DE 196 32 053 C2 another cooling system is known, which is designed as underfloor cooling system.

From the CH 296 227 A is known a radiator shutter for bi-directional rail vehicles, which is arranged at an air outlet in order to divert the exiting cooling air flow in the respective direction of travel of the vehicle can. The Venetian blind works passively, so it is controlled by the pressure forces acting on it.

From the DE 15 80 939 C3 For example, an intake-side ventilation grille for bidirectional rail vehicles is known, which has a multiplicity of fins which are variable in geometry as a function of the speed of the vehicle. If the ventilation grille is provided for a bidirectional rail vehicle, the individual slats are symmetrically shaped, resulting in symmetrical flow situations for both directions of travel.

Basically, there is a need to provide such a cooling system with a relatively large power. To generate a large cooling capacity, a correspondingly large-sized blower can be provided in principle in order to generate a correspondingly large flow of cooling air. However, this is precluded by soundproofing regulations, as powerful blowers often tend to produce a relatively large amount of noise.

The present invention is concerned with the problem of providing for a cooling system of the aforementioned type or for a rail vehicle equipped therewith an improved embodiment, which is characterized in particular by an increased efficiency of the cooling system or by improved cooling. Another aspect of the invention may be seen in providing a powerful refrigeration system that also operates comparatively quietly.

According to the invention, this problem is solved by the subject matter of the independent claim. Advantageous embodiments are the subject of the dependent claims.

The invention is based on the general idea to arrange the flow guide in the longitudinal direction over the entire air inlet side of the respective radiator, so that in the respective direction of travel of the cooling air flow is deflected to the entire permeable cross section of the radiator. In other words, the flow-guiding device is designed such that the flow-through cross-section controlled by it corresponds substantially to the entire flow-through cross-section of the radiator, so that in both directions of travel the cooling air flow can be conducted directly through the entire radiator. The expression "substantially" is understood to mean that the through-flowable cross-section of the flow-guiding device controlled by means of the flow-guiding device is at least 90% of the cross-section through which the radiator can flow in the horizontal transverse direction. Thus, a particularly efficient flow through the radiator can be realized for both directions, which improves the cooling capacity of the cooling system accordingly.

Since the flow of the cooler can be improved with the aid of the flow-guiding device arranged according to the invention, the cooling capacity can be increased without the need for a stronger blower for this purpose. Accordingly, the cooling system presented here can also manage with a weaker, quieter fan to produce the desired cooling capacity. Accordingly, with the help of the cooling system presented here also strict noise control provisions can be met.

The cooling system presented here is preferably used as a traction cooling system, so it is mainly used for cooling of drive units of the rail vehicle. Furthermore, the cooling system is designed so that it can use the airstream during the journey of the rail vehicle in order to generate or increase the cooling air flow. The cooling system is expediently used as a roof-mounted cooling system designed. Alternatively, the cooling system can also be designed as underfloor cooling system.

The relative figures "vertical", "horizontal", "top" and "bottom" here refer to a proper installation situation of the cooling system on the rail vehicle. The vertical direction then extends parallel to the direction of gravity. The horizontal direction extends transversely to the vertical direction. An orientation "down" occurs in the direction of gravity, while an orientation "up" is opposite thereto.

According to an advantageous embodiment, the flow-guiding device can have a plurality of guide vanes which are each pivotable about their own vertical pivot axis between a first blade position associated with the first shift position and a second blade position associated with the second shift position and distributed in the longitudinal direction over the entire air inlet side of the cooler , By using a plurality of vanes extending over the entire air inlet side, the flow guide device is comparatively compact and allows efficient flow diversion in the longitudinal direction over the entire air inlet side.

In a specific development, the respective guide vane may have two legs, which are arranged so as to be adjustable relative to one another about a hinge about an articulation axis, so that the respective guide vane can be adjusted by pivoting its legs about the articulation axis between the first vane position and the second vane position. This results in a particularly compact design.

According to a preferred alternative development, the respective guide blade can have a concavely curved guide contour exposed to the air flow or facing the air flow, transversely to the vertical direction. Such a concave curvature improves the flow deflection with a comparatively low flow resistance. At the same time, the air flow can be largely deflected laminar without an excessive vortex formation is to be feared. Accordingly, the air flow can pass through the radiator particularly efficiently.

In another development, the associated pivot axis can be arranged eccentrically to the guide vane in the respective vane. This can simplify the adjustability of the respective vane.

In another embodiment, it can be provided that, in the case of the respective guide blade, the associated pivot axis extends outside the respective guide blade. This measure can be used, for example, to simplify the control of the respective vane to their adjustment.

According to another embodiment, in the case of the respective guide blade, the pivot axis can run at a distance from the respective guide blade at a side facing the respective guide contour. This measure can also be used for simplified control of the respective vane. For example, the forces required to adjust the vane are reduced. Suitably, the respective pivot axis is symmetrical with respect to the associated guide vanes, in particular arranged in a mirror plane of the respective guide vane.

In another embodiment it can be provided that, in the first switching position and in the second switching position, a guide blade, which is first flown by the air flow in the longitudinal direction, is made smaller than the last flowed-on guide blade relative to the longitudinal direction. With identical guide vanes, this leads to the guide vanes diverting different regions of the incoming air flow from the longitudinal direction into the transverse direction, which improves the overall efficiency of the flow diversion.

According to an advantageous development, it can be provided that at least one further vane is arranged between the first impinged vane and the last impinged vane whose angle of attack relative to the longitudinal direction in the first switching position and in the second switching position between the angles of attack of the first streamed and the last streamed Guide vane is located. Suitably, all the guide vanes in the first switching position and in the second switching position have varying, preferably increasing angles of attack, from the first impinging vane to the last impinged vane.

In another embodiment, it may be provided that the respective vane has a vertically extending first end edge and a vertically extending second end edge, whereby the guide vanes have a geometrically comparatively simple structure. Furthermore, it can be provided that, in the first switch position, the first end edge is arranged proximal to the air inlet side of the respective radiator for all guide vanes, while the second end edge is arranged distally to the air inlet side. In the second switching position, the second end edges are then arranged proximal to the air inlet side in all guide vanes, while then the first end edges are arranged distally to the air inlet side. This results in a comparatively large pivoting range for the guide vanes, which due to the arrangement over the entire, measured in the longitudinal direction width of the radiator leads to an efficient flow in both switching positions.

In an advantageous development, it can be provided that in the first switching position and in the second switching position in the last impinged guide vane, the end edge arranged distally of the air inlet side has a larger distance from the air inlet side than in the first impinged vane. This measure also means that the individual guide vanes pick up different regions of the incoming, oriented in the longitudinal direction air flow and deflect in the transverse direction. This improves the efficiency of the flow deflection.

According to a particularly advantageous development, at least one further vane may be arranged between the first impinged vane and the last impinged vane, in which case the end edge, respectively distal to the air inlet side, from the air inlet side has a distance between the first inlet position and the second switch position the distances that are present at the last and the first impinged vane. In particular, it can thus be provided that in both switching positions, the distal end edges of all the guide vanes have different distances from the air inlet side. In particular, said distance always increases from the first impinged vane to the last impinged vane.

In another embodiment, it may be provided that in the first switch position and in the second switch position in all guide vanes, the end edges arranged in each case proximal to the air inlet side have the same distance from the air inlet side or abut against the air inlet side. This results in a comparatively complex arrangement of the guide vanes in the different switching positions. At the same time, this makes it possible to realize an intensive flow through the radiator.

In another embodiment, it may be provided that all guide vanes are coupled to one another, so that an adjustment of the guide vanes between the respective first vane position and the respective second vane position takes place simultaneously. In particular, an active adjustment by means of an adjusting device can thereby be implemented particularly easily, since, for example, only a single adjusting device has to be provided for adjusting all the guide vanes, which, as it were, can also be arranged as desired due to the mechanical coupling of the guide vanes.

Alternatively it can be provided that all guide vanes are individually and independently adjustable between the first vane position and the second vane position. In this case, a passive adjustability of the guide vanes may preferably be provided, in which the guide vanes are adjusted in each case depending on the dynamic pressure of the air flow acting thereon. Such a configuration of the flow-guiding device with passive adjustability of the guide vanes can be realized particularly inexpensively.

In another advantageous embodiment, at least one outflow-side flow-guiding device can be arranged on an air outlet side of the respective cooler, which is adjustable between a first switching position and a second switching position. In the first switching position, the downstream flow-guiding device deflects air from the air outlet side in a first outflow direction, which differs from the transverse direction, in the first direction of travel. In the second switching position, the downstream flow-guiding device deflects air from the air outlet side in a second outflow direction, which differs from the transverse direction, in the second direction of travel. Through a targeted flow diversion At the air outlet side, the cooling air flow can be released into the environment with reduced flow resistance. In particular, the vehicle speed or the airstream can be used to transfer the cooling air flow into the environment.

According to an advantageous development, the first outflow direction and the second outflow direction can be the same and be oriented either vertically upwards or vertically downwards. A vertically upwardly oriented outflow direction is preferred when the cooling system is designed as a roof-mounted cooling system. If, on the other hand, the cooling system is designed as an underfloor cooling system, a vertical downflow is preferred.

Alternatively, the first outflow direction may be opposite to the first direction of travel and the second outflow direction. In this case, the flow deflection takes place with the aid of the downstream flow guide from the transverse direction in the longitudinal direction, in each case against the respective direction of travel.

In another embodiment, at least one air outlet can be provided, through which the cooling air flow flows vertically upwards or downwards, depending on whether it is a roof construction system or an underfloor system.

Another advantageous embodiment is characterized by at least one fan for generating and / or supporting the cooling air flow, wherein the respective fan is preferably arranged downstream of the respective radiator. Suitably, the respective fan is a radial fan. In particular, when the outflow direction is oriented vertically.

An inventive bidirectionally operable rail vehicle, which is preferably a railcar, is equipped with at least one cooling system of the type described above. If this is a roof-mounted cooling system, this is arranged on a roof of the rail vehicle. However, if this is an underfloor cooling system, it is housed on or in an underfloor of the rail vehicle.

Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Fig. 1

eine Draufsicht eines Schienenfahrzeugs in einer stark vereinfachten, schaltplanartigen Darstellung,

Fig. 2

eine Längsansicht des Schienenfahrzeugs aus Fig. 1 ebenfalls in einer stark vereinfachten, schaltplanartigen Darstellung,

Fig. 3

eine Draufsicht wie in Fig. 1, jedoch bei einer anderen Ausführungsform des Schienenfahrzeugs,

Fig. 4

eine Längsansicht wie in Fig. 2, jedoch bei der in Fig. 3 gezeigten Ausführungsform des Schienenfahrzeugs,

Fig. 5

eine Draufsicht wie in Fig. 1, jedoch bei einer weiteren Ausführungsform des Schienenfahrzeugs,

Fig. 6

eine Draufsicht wie in Fig. 5, jedoch bei entgegengesetzter Fahrtrichtung,

Fig. 7

ein stark vereinfachter Querschnitt einer Kühlanlage des Schienenfahrzeugs im Bereich eines Kühlers und einer Strömungsleiteinrichtung,

Fig. 8

ein Querschnitt wie in Fig. 7, jedoch bei einer anderen Ausführungsform der Strömungsleiteinrichtung,

Fig. 9

ein vergrößertes Detail IX aus Fig. 8 zur Veranschaulichung einer Verschwenkbarkeit einer Leitschaufel der Strömungsleiteinrichtung,

Fig. 10

ein Querschnitt wie in Fig. 7, jedoch bei einer weiteren Ausführungsform der Strömungsleiteinrichtung,

Fig. 11

ein Querschnitt wie in Fig. 10, jedoch bei einer nochmals anderen Ausführungsform der Strömungsleiteinrichtung.

Show, in each case schematically,

Fig. 1

a top view of a rail vehicle in a highly simplified, schematics-like representation,

Fig. 2

a longitudinal view of the rail vehicle Fig. 1 also in a very simplified, schematics-like representation,

Fig. 3

a top view as in Fig. 1 but in another embodiment of the rail vehicle,

Fig. 4

a longitudinal view as in Fig. 2 , but at the in Fig. 3 shown embodiment of the rail vehicle,

Fig. 5

a top view as in Fig. 1 but in a further embodiment of the rail vehicle,

Fig. 6

a top view as in Fig. 5 , but in the opposite direction,

Fig. 7

a greatly simplified cross section of a cooling system of the rail vehicle in the region of a radiator and a flow guide,

Fig. 8

a cross section as in Fig. 7 but in another embodiment of the flow guide,

Fig. 9

an enlarged detail IX Fig. 8 to illustrate a pivotability of a guide vane of the flow guide,

Fig. 10

a cross section as in Fig. 7 but in a further embodiment of the flow guiding device,

Fig. 11

a cross section as in Fig. 10 but in yet another embodiment of the flow guide.

According to the Fig. 1 to 6 comprises a rail vehicle 1, which is preferably a railcar, at least one cooling system 2. The rail vehicle 1 is bidirectionally operable, so that it in a first direction of travel 3, in the Fig. 1 . 3 and 5 pointing to the right, as well as in an opposite second direction of travel 4 can be operated in the Fig. 1 . 3 and 6 points to the left. The cooling system 2 is arranged in the examples shown here on a roof 5 of the vehicle 1, so that it is a roof-mounted cooling system. In other embodiments, the cooling system 2 may also be designed as an underfloor cooling system, wherein it is then arranged on an underfloor 6 of the rail vehicle 1 and is integrated into the underfloor 6. The cooling system 2 is preferably used for cooling drive units of the vehicle 1, so that it is a particularly powerful traction cooling system. Alternatively, it is basically conceivable to use such a cooling system 1 for cooling a vehicle interior, in particular a passenger compartment. In the Fig. 2 and 4 are also a rail bed 7 with rails 8 indicated for the rail vehicle 1, on which wheels 9 of the vehicle 1 are guided and roll.

The cooling system 2 comprises according to the Fig. 1 to 11 at least one radiator 10. The radiator 10 is arranged on the vehicle 1, that it can be flowed through transversely to a longitudinal direction 11, that is, in a transverse direction 12 by a cooling air flow 13 indicated by arrows. The longitudinal direction 11 and the transverse direction 12 also extend horizontally and relate to the respective direction of travel 3, 4 of the vehicle 1. The longitudinal direction 11 extends parallel to the directions of travel 3, 4, the transverse direction 12 perpendicular thereto. Furthermore, the cooling system 2 is equipped with at least one inflow-side flow-guiding device 14. This is arranged on an air inlet side 15 of the radiator 10 and is adjustable between a first switching position S1 and a second switching position S2. In the first switching position S1, which in the Fig. 1 . 3 and 5 is reproduced, the Strömungsleiteinrichtung 14 causes a deflection of the cooling air flow 13 from the longitudinal direction 11 in the transverse direction 12 on the air inlet side 15. This first switching position S1 is provided for the first direction of travel 3 of the vehicle 1, so that the incoming cooling air flow of the first direction of travel. 3 oppositely oriented. In the second switching position S2, the in Fig. 6 is reproduced, the Strömungsleiteinrichtung 14 causes a deflection of the cooling air flow 13 from the longitudinal direction 11 in the transverse direction 12 on the air inlet side 15, wherein the second switching position S2 is provided for the second direction of travel 4 of the vehicle 1, so that the incoming cooling air flow 13 of the second direction of travel 4 oriented opposite.

In particular, at high speeds of the vehicle 1, the driving speed in conjunction with the respective direction of travel 3, 4 leads to an alignment of the incoming air flow 13 parallel to the longitudinal direction 11. This leads to the Strömungsleiteinrichtung 14 to a back pressure, with the aid of the flow guide 14 in the transverse direction 12 is deflected to guide the air flow 13 through the radiator 10. The air flow 13, which largely arises at high driving speed by the relative movement of the vehicle 1 to the environment, is often referred to as a wind.

The inflow-side flow-guiding device 14 is arranged distributed in the longitudinal direction 11 over the entire air inlet side 15 of the radiator 10, so that the flow-directing device 14 virtually controls the entire flow-through cross section of the radiator 10 or acts directly on the cooling air flow 13. Thus, in both directions of travel 3, 4, the entire flow-through cross section of the radiator 10 can be used for a comparatively large cooling air flow 13.

In the embodiments shown here, the flow-guiding device 14 has a plurality of guide vanes 16. In principle, two guide vanes 16 may be sufficient, but more preferably two guide vanes 16 are provided. In particular, more than four vanes 16 may be present. The guide vanes 16 are each adjustable between a first vane position and a second vane position. The first blade position is assigned to the first switching position S1 and can accordingly also be designated S1. The first blade position S1 is in the Fig. 7, 8 . 10 and 11 each indicated by a solid line. The second blade position is assigned to the second shift position S2 and can accordingly also be designated S2. In the Fig. 7, 8 . 10 and 11 the second blade position S2 is indicated by a broken line.

In the embodiments of the Fig. 1 to 10 the guide vanes 16 are each pivotable about their own vertical pivot axis 17 between the first blade position S1 and the second blade position S2. The pivot axes 17 are in the Fig. 7 to 10 shown. In these embodiments, the vanes 16 each have a blade body 18 which is inherently rigid and pivots generally about the respective pivot axis 17. At the in Fig. 11 On the other hand, it is provided to design the respective guide blade 16 in a multi-membered manner, in this case in two parts, so that the respective guide blade 16 has two legs 19, 20 which are pivotable relative to one another about a hinge axis 22 via a hinge or hinge 21. The bending axis 22 is vertical.

In the embodiments of the Fig. 7 to 9 which also the embodiments of Fig. 1 to 6 correspond, the respective vane 16 transverse to the vertical direction 23, which in the Fig. 2 and 4 is indicated by a double arrow, a guide contour 24, which faces the incoming cooling air flow 13 or suspended is curved and concave. Due to the curved guide contour 24, the flow deflection can be realized from the longitudinal direction 11 in the transverse direction 12 with a comparatively low flow resistance.

According to the Fig. 2 to 9 For each vane 16, the associated pivot axis 17 is arranged eccentrically to the vane 16 and outside the vane 16. Further, the respective pivot axis 17 extends at one of the respective guide contour 24 facing side spaced from the guide blade 16th

At the in Fig. 7 In the embodiment shown, the guide vanes 16 are symmetrically or uniformly adjustable, so that the guide vanes 16 have the same angle of attack 25 in both switching positions S1, S2 with respect to the longitudinal direction 11. The angle of attack 25 is in Fig. 7 exemplified in the middle vane 16 indicated. It corresponds to the angle between the longitudinal direction 11 and a profile direction 26 which is defined by a straight line passing through a first end edge 27 and a second end edge 28 of the vane 16.

In contrast, shows Fig. 8 an embodiment in which the various guide vanes 16 have different angles of incidence 25 with respect to the longitudinal direction 11. For example, if the first direction of travel 3 is present in a solid line, the guide vane 16 which is first streamed by the air flow 13 is in the direction of travel FIGS. 7 and 8 right, while the last impinged vane 16 is left. Is recognizable in Fig. 8 When the vehicle 1 moves against the broken lines in the second direction of travel 4, the first impinged vane 16 is on the left, while the last impinged on the left is the first impinged vane 16 with a smaller incidence relative to the longitudinal direction 11 Guide vane 16 is arranged right. Also in this case is in Fig. 8 recognizable that the first impinged guide vane 16 has a smaller angle of attack 25 with respect to the longitudinal direction 11 than the last impinged vane 16. In the example of Fig. 8 For example, three vanes 16 are indicated. Thus, there is a further or middle vane 16 between the first impinged vane 16 and the last impinged vane 16. Recognizable possesses this further or middle vane 16 in both switch positions S1 and S2 (same) Anstellwinkel 25, between the Anstellwinkeln 25 of the first flows against the guide vane 16 and the last impinged vane 16 is located.

According to Fig. 9 is the pivot axis 17 in the middle vane 16 of the embodiment according to Fig. 8 or at each vane 16 of the embodiment according to Fig. 7 in a mirror symmetry plane 29, to which the respective guide blade 16 is arranged mirror-symmetrically. Further, for the middle vane 16 at the in Fig. 8 shown embodiment, the pivot axis 17 according to Fig. 9 positioned so as to define the center M of a perimeter 30 on which both the first end edge 27 and the second end edge 28 move about the pivot axis 17 as the vane 16 pivots. As a result, the same angle of attack 25 with respect to the longitudinal direction 11 results for the middle guide blade 16 for both directions of travel 3, 4. For all other guide blades 16 of the embodiment according to FIG Fig. 8 the two end edges 27, 28 move on different circular paths. So is in Fig. 8 for the left vane 16, a first circle 31 indicated, which follows the first end edge 27, while the second end edge 28 follows a second circle 32 having a different, here larger radius. Both circles 31, 32 are arranged concentrically with each other, wherein its center M is defined by the pivot axis 17.

How the FIGS. 7 and 8 2, the first end edges 27 are each arranged proximally to the air inlet side 15 of the radiator 10, while the respective second end edge 28 is arranged distally to the air inlet side 15 in all guide vanes 16 in the first switching position S1 (solid line). In the second switching position S2 (with a broken line), however, it behaves vice versa. In this case, for all the vanes 16, the first end edges 27 are then positioned distal to the air inlet side 15, while the second end edges 28 are disposed proximal to the air inlet side 15. At the in Fig. 7 In the embodiment shown, the end edges 27 (in the case of S2) and 28 (in the case of S1) arranged in each case distally to the air inlet side 15 are equidistant from the air inlet side 15. A corresponding distance is designated by A. In contrast, shows Fig. 8 an embodiment in which the distal end edges 27 (at S2) and 28 (at S1) of the individual guide vanes 16 have different distances A to the air inlet side 15. Thus, depending on the direction of travel 3, 4, the distal end edge 27 (at S2) and 28 (at S1) of the first impinged guide vane 16 closer to the air inlet side 15 is arranged as in the last impinged vane 16. Also provided here that in the middle guide blade 16 is also a mean distance A between the air inlet side 15 and the respective distal end edge 27 (at S2) and 28 (at S1) is present.

At the in Fig. 10 In the embodiment shown, the guide vanes 16 are each designed with a straight-line profile. Further, the associated pivot axis 17 extends within the guide vane 16, preferably in the region of the second end edge 28, which is arranged in this embodiment always distal to the air inlet side 15 and does not change their position regardless of the switching positions S1, S2. In Fig. 10 In addition, a mechanical forced coupling 33 of all vanes 16 is indicated together. Furthermore, an actuator not shown here for joint adjustment of all vanes 16th be provided. In addition, a spring means 34 may be provided to bias the vanes 16 in the respective switching position S1, S2.

In the embodiments of the Fig. 7 to 9 In addition, it is provided that the respective proximal end edge 27 (at S1) or 28 (at S2) is located directly at the air inlet side 15. In particular, the guide vanes 16 with their respective proximal end edge 27 (at S1) or 28 (at S2) can be supported directly on the radiator 10.

At the in Fig. 11 In the embodiment shown, each vane 16 may be provided with spring means 35 for biasing the respective vane 16 into a kinked position which then represents the respective vane position S1 and S2, respectively. For example, the spring device 35 may be a spring which connects the two end edges 27, 28 with each other. In particular, it may be provided in this case that all vanes 16 are uncoupled, so that they can be individually and independently adjusted between the first blade position S1 and the second blade position S2. In particular, such an adjustment can be made passively, so that it is possible to dispense with a separate actuator. For example, the air forces acting on the guide vanes 16 can bring about a corresponding adjustment of the guide vanes 16.

In principle, at high vehicle speeds, the airstream may be sufficient to generate the air flow 13, so that it flows through the radiator 10 with sufficient volumetric flow. However, especially for lower vehicle speeds, the cooling system 1 is expediently equipped with at least one blower 36 in order to generate or support the air flow 13. Suitably, the respective blower 36 is disposed downstream of the radiator 10. In the example of Fig. 1 and 2 is the respective fan 36 in a housing 37, which has an air outlet 38, through which the cooling air flow 13 is discharged in this case vertically upward from the blower 36.

In the in the 3 and 4 In contrast, a further downstream or downstream flow-guiding device 39 is provided which is arranged on an air outlet side 40, preferably downstream of the respective fan 36 and in particular on the air outlet 38 of the housing 37. In the example of 3 and 4 the outlet 38 is not oriented upwards as in the Fig. 1 and 2 , but also in the transverse direction 12. The downstream flow guide 39 is expediently identically constructed as the inflow-side flow guide 14. In particular, it is thus between one in the 3 and 4 indicated first switching position S1 and a second switching position (S2), not shown here adjustable. In the first switching position S1, which is provided for the first direction of travel 3, causes the downstream Strömungsleiteinrichtung 39, a deflection of the air flow 13 from the air outlet side 40 in a first outflow direction 41, in Fig. 3 is indicated by an arrow drawn by a solid line. In the second switching position (not shown), however, causes the downstream Strömungsleiteinrichtung 39, a deflection of the air flow 13 in a different direction from the transverse direction 12 second outflow direction 42, the in Fig. 3 is indicated by an arrow drawn with a broken line. In this example, the first outflow direction 41 is thus opposite to the first direction of travel 3. The second outflow direction 42 is opposite to the second direction of travel 4. Furthermore, the first outflow direction 41 of the second outflow direction 42 is opposite. Both outflow directions 41, 42 run essentially parallel to the longitudinal direction 11.

Claims (19)

Cooling system for a bidirectional rail vehicle (1), - With at least one cooler (10) which extends transversely to a longitudinal direction (11) in the installed state of the cooling system (2) parallel to the respective direction of travel (3, 4) of the vehicle (1), and horizontally by a cooling air flow (13 ) can be flowed through, - With at least one upstream Strömungsleiteinrichtung (14) which is arranged on an air inlet side (15) of the radiator (10) and between a first switching position (S1), in which they in a first direction of travel (3) of the rail vehicle (1) air from the longitudinal direction (11) in the transverse direction (12) on the air inlet side (15) deflects, and a second switching position (S2) is adjustable, in which they in a second direction (4) of the rail vehicle (1) air from the longitudinal direction ( 11) in the transverse direction (12) on the air inlet side (15) deflects, characterized,
in that the flow-guiding device (14) extends in the longitudinal direction (11) over the entire air inlet side (15) of the respective radiator (10). Cooling system according to claim 1,
characterized,
in that the flow-guiding device (14) has a plurality of guide vanes (16) which each between a first vane position assigned to the first switching position (S1) and a second one assigned to the second switching position (S2) Can be adjusted blade position and in the longitudinal direction (11) over the entire air inlet side (15) of the radiator (10) are arranged distributed. Cooling system according to claim 2,
characterized,
in that the respective guide blade (16) has two legs (19, 20) which are arranged so as to be adjustable relative to one another about a hinge axis (22) so that the respective guide blade (16) can be pivoted by pivoting its legs (19, 20 ) about the bending axis (22) between the first blade position (S1) and the second blade position (S2) are adjustable. Cooling system according to claim 2,
characterized,
that the respective guide vane (16) each about its own vertical pivot axis (17) (S1) and the second vane position (S2) is pivotable between the first blade position. Cooling system according to claim 4,
characterized,
that the respective guide blade (16) transverse to the vertical direction (23) of the air flow (13) exposed concave guiding contour (24). Cooling system according to claim 4 or 5,
characterized, - That at the respective guide vane (16), the associated pivot axis (17) is arranged eccentrically to the guide vane (16), and / or - That at the respective vane (16), the associated pivot axis (17) outside the respective vane (16) extends, and / or - that the pivot axis at the respective vane (16) (17) on a side facing the respective guide contour (24) side spaced apart from the respective guide vane (16). Cooling system according to one of claims 2 to 6,
characterized,
that in the first switch position (S1) and in the second switch position (S2) a in the longitudinal direction (11) from the air stream (13) first at zero incidence vane (16) relative to the longitudinal direction (11) is less employed as a most recently flowed vane (16 ). Cooling system according to claim 7,
characterized,
in that at least one further guide vane (16) is arranged between the first impinged vane (16) and the last impinged vane (16) whose angle of incidence (25) relative to the longitudinal direction (11) in the first switching position (S1) and in the second switching position (S2) between the angle of attack (25) of the first impinged vane (16) and the angle of attack (25) of the last impinged vane (16). Cooling system according to one of claims 2 to 8,
characterized, - That the respective vane (16) has a vertically extending first end edge (27) and a vertically extending second end edge (28), in that, in the first switching position (S1), in each case the first end edge (27) is arranged proximal to the air inlet side (15) of the respective radiator (10), while the second end edge (28) extends distally to the air inlet side (15) is arranged in that, in the second switching position (S2), the second end edge (28) is arranged proximal to the air inlet side (15) of the respective radiator (10) for all guide vanes (16), while the first end edge (27) extends distally to the air inlet side (15) is arranged. Cooling system according to claim 9,
characterized,
that in the first switch position (S1) and in the second switch position (S2) in the last-incident flow guide vane (16) arranged each distal to the air intake side (15) end edge (27, 28) a greater distance (A) from the air inlet side (15 ) than in the first impinged vane (16). Cooling system according to claim 10,
characterized,
that a further vane (16) is arranged between the first incident flow guide vane (16) and the last incident flow guide vane (16) at least when in the first switch position (S1) and in the second switch position (S2) each having distal (to the air inlet side 15) arranged end edge (27, 28) from the air inlet side (15) has a distance (A) which lies between the distances (A), which are present at the last impinged vane (16) and the first impinged vane (16). Cooling system according to one of claims 9 to 11,
characterized,
that in the first switch position (S1) and in the second switch position (S2) for all guide vanes (16) arranged respectively proximate to the air inlet side (15) end edges (27, 28) have the same distance from the air inlet side (15) or at the air inlet side (15) are present. Cooling system according to one of claims 2 to 12,
characterized,
in that all the guide vanes (16) are coupled to one another such that an adjustment of the guide vanes (16) between the respective first vane position (S1) and the respective second vane position (S2) takes place simultaneously. Cooling system according to one of claims 2 to 12,
characterized,
that all vanes (16) (S1) and the second vane position (S2) are adjustable individually and independently of each other between the first blade position. Cooling system according to one of claims 1 to 14,
characterized,
in that at least one outflow-side flow-guiding device (39) is arranged on an air outlet side (40) of the respective radiator (10) between a first switching position (S1) in which air is supplied from the air outlet side (40) in the first direction of travel (3) one deflects from the transverse direction (12) different first outflow direction (41), and a second switching position (S2) is adjustable, in which they in the second direction of travel (4) air from the air outlet side (40) in one of the transverse direction (12) different second outflow direction (42) deflects. Cooling system according to claim 15,
characterized, - that the first outflow (41) and the second outflow (42) are identical and are oriented vertically upwards or downwards, or - That the first outflow direction (41) of the first direction of travel (3) and the second direction of travel (42) is opposite. Cooling system according to one of claims 1 to 16,
characterized,
in that at least one air outlet (38) is provided, through which the cooling air flow (13) flows vertically upwards or downwards. Cooling system according to one of claims 1 to 17,
marked by
at least one fan (36) for generating and / or supporting the cooling air flow (13), which is preferably arranged downstream of the respective radiator (10) and which is designed in particular as a radial fan. Bidirectionally operable rail vehicle (1) with a roof (5), with an underfloor (6) and with at least one cooling system (2) according to one of the preceding claims.

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