EP3059135A1 - Vehicule sur rail dote d'un systeme de refroidisseur - Google Patents

Vehicule sur rail dote d'un systeme de refroidisseur Download PDF

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Publication number
EP3059135A1
EP3059135A1 EP15201035.1A EP15201035A EP3059135A1 EP 3059135 A1 EP3059135 A1 EP 3059135A1 EP 15201035 A EP15201035 A EP 15201035A EP 3059135 A1 EP3059135 A1 EP 3059135A1
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EP
European Patent Office
Prior art keywords
vane
cooling system
air inlet
inlet side
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP15201035.1A
Other languages
German (de)
English (en)
Inventor
Stefan Frank
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP3059135A1 publication Critical patent/EP3059135A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
    • B61D27/00—Heating, cooling, ventilating, or air-conditioning

Definitions

  • 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.
  • 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.
  • 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.
  • the flow guiding device deflects air from the longitudinal direction in the transverse direction to the air inlet side.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • an intake-side ventilation grille for bidirectional rail vehicles 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.
  • 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.
  • 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.
  • 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.
  • 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 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 ,
  • the flow guide device is comparatively compact and allows efficient flow diversion in the longitudinal direction over the entire air inlet side.
  • 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.
  • 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.
  • a concave curvature improves the flow deflection with a comparatively low flow resistance.
  • 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.
  • 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.
  • 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.
  • the pivot axis in the case of the respective guide blade, 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the distal end edges of all the guide vanes have different distances from the air inlet side.
  • said distance always increases from the first impinged vane to the last impinged vane.
  • 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.
  • 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.
  • 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.
  • all guide vanes are individually and independently adjustable between the first vane position and the second vane position.
  • 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.
  • 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.
  • 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.
  • 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.
  • the cooling air flow can be released into the environment with reduced flow resistance.
  • the vehicle speed or the airstream can be used to transfer the cooling air flow into the environment.
  • 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.
  • the first outflow direction may be opposite to the first direction of travel and the second outflow direction.
  • 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.
  • 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.
  • 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.
  • 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.
  • a cooling system 1 for cooling a vehicle interior, in particular a passenger compartment.
  • 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.
  • 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.
  • the Strömungsleit listening 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.
  • the second switching position S2 the in Fig. 6 is reproduced, the Strömungsleit Huawei 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.
  • 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.
  • 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.
  • the entire flow-through cross section of the radiator 10 can be used for a comparatively large cooling air flow 13.
  • the flow-guiding device 14 has a plurality of guide vanes 16.
  • 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.
  • 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.
  • the vanes 16 each have a blade body 18 which is inherently rigid and pivots generally about the respective pivot axis 17.
  • 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.
  • 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.
  • 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
  • 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.
  • FIG. 8 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.
  • 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.
  • Guide vane 16 is arranged right. Also in this case is in Fig.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 8 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a spring means 34 may be provided to bias the vanes 16 in the respective switching position S1, S2.
  • the respective proximal end edge 27 (at S1) or 28 (at S2) is located directly at the air inlet side 15.
  • 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.
  • 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.
  • the spring device 35 may be a spring which connects the two end edges 27, 28 with each other.
  • 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.
  • the air forces acting on the guide vanes 16 can bring about a corresponding adjustment of the guide vanes 16.
  • the airstream may be sufficient to generate the air flow 13, so that it flows through the radiator 10 with sufficient volumetric flow.
  • the cooling system 1 is expediently equipped with at least one blower 36 in order to generate or support the air flow 13.
  • the respective blower 36 is disposed downstream of the radiator 10.
  • 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.
  • 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.
  • 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.
  • first switching position S1 which is provided for the first direction of travel 3 causes the downstream Strömungsleit responded 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.
  • second switching position (not shown), however, causes the downstream Strömungsleit Huawei 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
EP15201035.1A 2015-02-17 2015-12-18 Vehicule sur rail dote d'un systeme de refroidisseur Withdrawn EP3059135A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015202815.1A DE102015202815A1 (de) 2015-02-17 2015-02-17 Schienenfahrzeug mit Kühlanlage

Publications (1)

Publication Number Publication Date
EP3059135A1 true EP3059135A1 (fr) 2016-08-24

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EP15201035.1A Withdrawn EP3059135A1 (fr) 2015-02-17 2015-12-18 Vehicule sur rail dote d'un systeme de refroidisseur

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EP (1) EP3059135A1 (fr)
DE (1) DE102015202815A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113085928A (zh) * 2021-03-05 2021-07-09 中车（天津）轨道交通设备有限公司 一种翻板式通风除尘装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT521090B1 (de) * 2018-03-07 2020-04-15 Siemens Mobility Austria Gmbh Unterflurgeräteträger für ein Schienenfahrzeug

Citations (9)

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Publication number Priority date Publication date Assignee Title
DE523925C (de) 1930-01-03 1931-05-01 Fried Krupp Akt Ges Durch eine Brennkraftmaschine angetriebene Lokomotive
CH296227A (de) 1943-08-23 1954-01-31 Daimler Benz Ag In beiden Fahrtrichtungen wirksame Kühlerjalousie an Fahrzeuglängswänden, insbesondere von Schienenfahrzeugen.
AU1639676A (en) * 1976-07-29 1978-02-02 Bernard J E Jr Twin ventilator for railroad car
US4219071A (en) * 1978-05-26 1980-08-26 Wabco Westinghouse S.P.A. Air-conditioning system for railroad vehicles
DE1580939C3 (de) 1967-08-05 1981-07-02 Krauss-Maffei AG, 8000 München Lüftungsgitter für Fahrzeuge, insbesondere für Schienenfahrzeuge
DE4405377A1 (de) * 1993-03-04 1994-09-08 Jenbacher Transportsysteme Kühleinrichtung für Fahrzeuge, insbesondere für Schienenfahrzeuge
DE19632053C2 (de) 1996-08-08 2000-10-05 Voith Turbo Beteiligungs Gmbh Unterflurkühlanlage und Verfahren zur Kühlung elektrischer Leistungsbauteile in Schienenfahrzeugen
WO2010140791A2 (fr) * 2009-06-05 2010-12-09 Ko Hong-Dal Appareil de refroidissement pour un train
WO2011050616A1 (fr) * 2009-10-31 2011-05-05 中国北车集团大连研究所有限公司 Dispositif de refroidissement aérien

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Publication number Priority date Publication date Assignee Title
US1098329A (en) * 1912-12-30 1914-05-26 Stone J & Co Ltd Ventilating means for railway and other vehicles.
DE677974C (de) * 1937-06-11 1939-07-05 Julius Pintsch Kom Ges Belueftung von Fahrzeugen, insbesondere von Eisenbahnfahrzeugen

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE523925C (de) 1930-01-03 1931-05-01 Fried Krupp Akt Ges Durch eine Brennkraftmaschine angetriebene Lokomotive
CH296227A (de) 1943-08-23 1954-01-31 Daimler Benz Ag In beiden Fahrtrichtungen wirksame Kühlerjalousie an Fahrzeuglängswänden, insbesondere von Schienenfahrzeugen.
DE1580939C3 (de) 1967-08-05 1981-07-02 Krauss-Maffei AG, 8000 München Lüftungsgitter für Fahrzeuge, insbesondere für Schienenfahrzeuge
AU1639676A (en) * 1976-07-29 1978-02-02 Bernard J E Jr Twin ventilator for railroad car
US4219071A (en) * 1978-05-26 1980-08-26 Wabco Westinghouse S.P.A. Air-conditioning system for railroad vehicles
DE4405377A1 (de) * 1993-03-04 1994-09-08 Jenbacher Transportsysteme Kühleinrichtung für Fahrzeuge, insbesondere für Schienenfahrzeuge
DE19632053C2 (de) 1996-08-08 2000-10-05 Voith Turbo Beteiligungs Gmbh Unterflurkühlanlage und Verfahren zur Kühlung elektrischer Leistungsbauteile in Schienenfahrzeugen
WO2010140791A2 (fr) * 2009-06-05 2010-12-09 Ko Hong-Dal Appareil de refroidissement pour un train
WO2011050616A1 (fr) * 2009-10-31 2011-05-05 中国北车集团大连研究所有限公司 Dispositif de refroidissement aérien

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113085928A (zh) * 2021-03-05 2021-07-09 中车（天津）轨道交通设备有限公司 一种翻板式通风除尘装置

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