EP3514812B1 - Transformator für fahrzeug - Google Patents

Transformator für fahrzeug Download PDF

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Publication number
EP3514812B1
EP3514812B1 EP16916188.2A EP16916188A EP3514812B1 EP 3514812 B1 EP3514812 B1 EP 3514812B1 EP 16916188 A EP16916188 A EP 16916188A EP 3514812 B1 EP3514812 B1 EP 3514812B1
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EP
European Patent Office
Prior art keywords
cooling
header
pipe group
inlet
outlet
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Active
Application number
EP16916188.2A
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English (en)
French (fr)
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EP3514812A4 (de
EP3514812A1 (de
Inventor
Akihiro Nagase
Sunao Kato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3514812A1 publication Critical patent/EP3514812A1/de
Publication of EP3514812A4 publication Critical patent/EP3514812A4/de
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Publication of EP3514812B1 publication Critical patent/EP3514812B1/de
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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F27/00—Details of transformers or inductances, in general
    • H01F27/08—Cooling; Ventilating
    • H01F27/10—Liquid cooling
    • H01F27/12—Oil cooling
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F27/00—Details of transformers or inductances, in general
    • H01F27/02—Casings
    • H01F27/025—Constructional details relating to cooling
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F38/00—Adaptations of transformers or inductances for specific applications or functions

Definitions

  • This invention relates to a traction transformer which is to be installed on a roof of a vehicle, in particular, a traction transformer which includes a cooler configured to cool cooling medium stored in a transformer tank through use of traveling wind generated by traveling of a vehicle.
  • Devices such as an air conditioner, an exchanger, a controller, and a transformer, which are to be mounted to a vehicle, generate a large amount of heat during operations, and hence cooling of the devices is required.
  • Methods of cooling those devices mainly include a forcible air-cooling method using a blower and a traveling-wind self-cooling method using traveling wind generated by traveling of a vehicle.
  • the traveling-wind self-cooling method attracts attention.
  • a cooler for a vehicle employing the traveling-wind self-cooling method in consideration of ease of manufacture and ease of maintenance, a cooler including heat rejection pipes, which each have a U-shape and are arrayed in a plurality of stages, is employed in many cases (see, e.g. Patent Literature 1).
  • Such a cooler includes a plurality of heat rejection pipes to increase an area for heat exchange with cooling wind and thereby secure high heat-rejection performance.
  • the size of the cooler differs depending on an installation location thereof and maximum heat generation amounts of the devices.
  • a cooler volume of about 0.5 m 3 and a wind-guiding distance of about 1 m for guiding wind are required.
  • Such cooler includes heat rejection pipes each having a plurality of fins mounted thereto, and a heat rejection area per unit volume can be increased.
  • Patent Literature 3 discloses a cooling device of a transformer for vehicle, aiming for improving the cooling performance, by arranging two coolers on both sides of a transformer main body and by equalising the length of all oil passages.
  • This invention has been made to solve the problems described above, and has an object to obtain a traction transformer which is capable of achieving efficient cooling through use of traveling wind generated by traveling of a vehicle while reducing an installation space for installation on a roof of a vehicle.
  • the traction transformer which is capable of achieving efficient cooling through use of traveling wind generated by traveling of the vehicle while reducing an installation space for installation on the roof of the vehicle.
  • FIG. 1 is a top view for illustrating a railway vehicle 1 including a traction transformer 10 according to a first example which is not part of the present invention, which is installed on a roof 2.
  • FIG. 2 is a side view for illustrating the railway vehicle including the traction transformer 10 according to the first example which is not part of the present invention, which is installed on the roof 2.
  • FIG. 3 is an enlarged perspective view for illustrating a periphery of the traction transformer 10 which is installed on the railway vehicle 1 of FIG. 1 and FIG. 2 .
  • FIG. 4 is a top view of the traction transformer 10 of FIG. 3 .
  • FIG. 5 is a side view of the traction transformer 10 of FIG. 3 .
  • the railway vehicle 1 is simply referred to as “vehicle 1”, and the traction transformer 10 is simply referred to as “transformer 10".
  • a length direction of the vehicle 1, that is, an advancing direction of the vehicle 1 is referred to as "X direction”.
  • a vehicle width direction of the vehicle 1 is referred to as "Y direction”
  • a height direction of the vehicle is referred to as "Z direction”. That is, the vehicle 1 can travel in both a +X direction and a -X direction.
  • a +Z direction corresponds to the roof 2 side
  • a -Z direction corresponds to a floor side.
  • the transformer 10 includes a winding wire 11, a main pipe 12, a transformer tank 13, a circulation pump 14, and a cooler 15.
  • the transformer 10 is installed on the roof 2 of the vehicle 1.
  • peripheral devices 3 such as a converter, a controller, and an air conditioner are installed on the roof 2 in the +X direction and the -X direction of the transformer 10.
  • the winding wire 11 is accommodated in the transformer tank 13.
  • the main pipe 12 forms a circulation passage for refrigerant.
  • the transformer tank 13 is arranged midway of the circulation passage formed of the main pipe 12, and is configured to accommodate the winding wire 11 and store the refrigerant inside thereof.
  • the transformer tank 13 is installed at the center in the Y direction on the roof 2 of the vehicle 1.
  • the circulation pump 14 is arranged midway of the circulation passage formed of the main pipe 12, and is configured to circulate the refrigerant in the circulation passage.
  • the circulation pump 14 is installed in the X direction of the transformer tank 13.
  • the cooler 15 is arranged midway of the circulation passage formed of the main pipe 12, and is configured to cool the refrigerant by heat exchange with air, specifically, by heat exchange with traveling wind generated at the time of traveling of the vehicle 1. Moreover, the cooler 15 is installed on an upper surface of the transformer tank 13, that is, on a +Z direction surface. An inlet side of the cooler 15 is connected to an inlet-side pipe 12a forming the main pipe 12, and an outlet side of the cooler 15 is connected to an outlet-side pipe 12b forming the main pipe 12.
  • the transformer tank 13 is a box having a rectangular parallelepiped shape.
  • the transformer tank 13 accommodates the winding wire 11 inside thereof and is made of metal such as steel or aluminum.
  • a surface of the transformer tank 13 has coating for prevention of corrosion, and has, for example, a bush for connection of an electric wire.
  • insulating oil is generally used as refrigerant.
  • silicone oil having high non-combustibility or ester oil being advantageous in environment is used as refrigerant for vehicles.
  • FIG. 6 is a sectional view taken along the line A-A' of FIG. 5 as seen in the direction indicated by the arrows.
  • FIG. 7 is an explanatory view for illustrating a flow of traveling wind on a rear side of the peripheral device 3 in the advancing direction on the roof 2 of the railway vehicle 1 in the first example which is not part of the present invention.
  • FIG. 8 is a contour diagram for illustrating, in vehicle cross section, a wind velocity on the rear side of the peripheral device 3 in the advancing direction on the roof 2 of the railway vehicle 1 in the first example which is not part of the present invention.
  • a vehicle body cross section of the vehicle 1, that is, a Y-Z cross section has limit values in the Y direction and the Z direction, that is, a rolling stock gauge 4 defined therefor. That is, a cross section of the vehicle 1 is required to be provided within the range of the rolling stock gauge 4.
  • the rolling stock gauge 4 is a reference that is defined for avoiding interference between a vehicle body and a construction provided along a railway track. In relation to construction of tunnels, in many cases, the vehicle 1 has such a shape that an upper side of the roof 2, that is, the +Z direction side of the roof 2 is narrow.
  • the peripheral device 3 is designed so as to project to a maximum dimension falling within the rolling stock gauge 4.
  • the transformer 10 In order to supply an overhead wiring voltage exceeding 20 000 Volt to a main circuit, the transformer 10 utilizes the principle of electromagnetic induction to step down the voltage. Moreover, the outer dimensions of the transformer 10 are determined based on the size of the winding wire 11, which is determined based on a frequency of overhead wiring power and a conversion efficiency of the transformer 10.
  • the winding wire 11 is accommodated in the transformer tank 13 having the rectangular parallelepiped shape.
  • the rolling stock gauge 4 has a trapezoidal shape as illustrated in FIG. 6 .
  • a space in which the devices can be arranged is defined by the upper surface side, that is, the +Z direction side of the transformer tank 13 and the side surface sides, that is, the +Y direction side and the -Y direction side of the transformer tank 13.
  • the main pipe 12 and a support structure body are arranged on the side surface sides of the transformer tank 13.
  • FIG. 7 schematic illustration is given of a state in which a traveling wind 5 is separated by the peripheral device 3 installed on the roof 2 of the vehicle 1. It is assumed that the traveling wind 5 flows in the -X direction.
  • the traveling wind 5 separated by the peripheral device 3 having a height h gradually approaches the roof 2 as proceeding toward downstream of a flow field, and is brought into contact with the roof 2 at a re-contact point 6.
  • a distance x from separation to re-contact is about seven times the height h of the peripheral device 3, that is, about 7h.
  • a vortex is less liable to be generated in the flow field on the roof 2 of the vehicle 1 being an open space. Therefore, in consideration of arranging the cooler on downstream of the peripheral device 3, a sufficient wind-guiding distance is required for obtaining traveling wind flowing at high flow velocity.
  • FIG. 8 illustration is given of, for each x coordinate, a relationship between wind velocity distribution on the Y-Z plane after separation by the peripheral device 3 arranged so as to extend along the rolling stock gauge 4 and the inner side and the outer side of the rolling stock gauge 4.
  • the re-contact of the main stream does not proceed at the position of about 1 m after separation, and it can be seen that wind flowing at high wind velocity is obtained only in the vicinity of a boundary of the rolling stock gauge 4.
  • the roof 2 of the vehicle 1 has a complicated shape.
  • the course of re-contact is not as simple as that on downstream of the step, but a stagnation region 7 is formed after separation. Therefore, when the transformer 10 is arranged close to the peripheral device 3, sufficient wind velocity required for cooling can be obtained only in a region in a periphery of the boundary of the rolling stock gauge 4.
  • An allowable device arrangement height on the roof 2 is about 1 m at maximum.
  • the transformer tank 13 has a height of 0.7 m
  • a space having a height of about 0.3 m can be secured between the upper surface of the transformer tank 13 and the rolling stock gauge 4.
  • This space is a space in which traveling wind flows at high velocity even when the transformer 10 is arranged close to the peripheral device 3. Therefore, when the cooler, which has hitherto been arranged separately, is arranged in this space, the wind-guiding distance can be minimized, and hence there is given a significant merit in view of the installation space of the transformer 10.
  • the cooler 15 is installed on the upper surface of the transformer tank 13. Further, a structure of the cooler 15 is devised so that required cooling performance can be obtained.
  • FIG. 9 is a perspective view for illustrating the cooler 15 in the first example which is not part of the present invention.
  • the cooler 15 includes an inlet header 16a, an outlet header 16b, and a direct cooling-pipe group 18.
  • the inlet header 16a is configured to allow the refrigerant to flow thereinto from the circulation pump 14 side.
  • the outlet header 16b is configured to allow the refrigerant to flow out to the transformer tank side.
  • the direct cooling-pipe group 18 includes a plurality of cooling pipes 17, which are arranged so as to allow the refrigerant to flow out from the inlet header 16a and flow into the outlet header 16b.
  • a mechanism which is formed of a group of a plurality of cooling pipes that form flow passages between the inlet header 16a and the outlet header 16b and are configured to cool the refrigerant flowing through the flow passages, is referred to as "cooling-pipe mechanism".
  • cooling-pipe mechanism includes the direct cooling-pipe group 18, which is formed of the plurality of cooling pipes 17 elongated in the Y direction and arrayed in a plurality of rows in the X direction and connects the inlet header 16a and the outlet header 16b to each other.
  • the inlet header 16a and the outlet header 16b have a longitudinal direction extending in the X direction and are installed on the transformer tank 13 while being separated from each other in the Y direction and being parallel to each other.
  • the direct cooling-pipe group 18 is formed of the plurality of cooling pipes 17, which each have a U-shape protruding in the +Z direction and are arrayed in a plurality of rows in the X direction.
  • the cooling pipes 17 are provided in the Z direction (upper side) from the upper surface of the transformer tank 13.
  • the cooling pipes 17 are elongated in the Y direction.
  • six U-shaped cooling pipes 17 having different sizes are arranged on the Y-Z plane, and the rows each including the six U-shaped cooling pipes 17 are arrayed at a constant pitch along the X direction.
  • the six cooling pipes 17 of each of the rows forming the direct cooling-pipe group 18 have different heights in the Z direction and widths in the Y direction, but the flow passages thereof have the same sectional shape.
  • the number of arrays of the cooling pipes 17 and pitches thereof may suitably be changed.
  • each of the cooling pipes 17 the refrigerant having been increased in temperature due to heat received from, for example, the winding wire 11 flows therethrough.
  • Each of the cooling pipes 17 has one end connected to the inlet header 16a and another end connected to the outlet header 16b.
  • the rows of the direct cooling-pipe group 18 are arrayed in the X direction, and hence the inlet header 16a and the outlet header 16b each have a shape elongated in the X direction.
  • the inlet header 16a is connected to the circulation pump 14, receives the refrigerant supplied from the circulation pump 14, and distributes the refrigerant to the cooling pipes 17.
  • the outlet header 16b is connected so as to gather the refrigerant having flowed through the cooling pipes 17 and return the gathered refrigerant to the transformer tank 13.
  • the six cooling pipes 17 forming each of the rows of the direct cooling-pipe group 18 each include a first bent portion, a second bent portion, and a coupling portion.
  • the first bent portion is bent with respect to the inlet header 16a from the +Z direction toward the +Y direction side.
  • the second bent portion is bent with respect to the outlet header 16b from the +Z direction toward the -Y direction side.
  • the coupling portion couples the first bent portion and the second bent portion to each other in parallel with a horizontal plane.
  • the first bent portion and the second bent portion are perpendicularly connected to the inlet header 16a and the outlet header 16b, respectively. However, it is not always required that the first bent portion and the second bent portion be connected to the inlet header 16a and the outlet header 16b in such a manner.
  • the coupling portion is in parallel with the horizontal plane. However, it is not always required that the coupling portion be provided in such a manner. For example, the coupling portion may have a gentle arch shape.
  • pipes each having a flat shape are used as the cooling pipes 17, and the flat surfaces thereof extend along the X direction.
  • the cooling pipes 17 are used as described above, the cooling performance is improved.
  • circular pipes may be used as the cooling pipes 17.
  • a space is defined below the direct cooling-pipe group 18. That is, a gap is defined between the coupling portions of the cooling pipes 17 arranged on an innermost side of the rows and the upper surface of the transformer tank 13. As illustrated in FIG. 9 , the coupling portions of the cooling pipes 17 extend along the Y direction. Therefore, the space defined below the rows of the direct cooling-pipe group 18 is a space which is opened so as to be elongated in the Y direction with respect to the Z direction. In the following description, the space defined below the cooling pipes 17 is referred to as "opening space 19".
  • the direct cooling-pipe group 18 is arranged at a high position on the upper surface of the transformer tank 13. Therefore, even when any other devices are arranged on the front and rear sides, the direct cooling-pipe group 18 can successfully cool the refrigerant through use of the traveling wind. Moreover, when the traveling wind is not given, that is, when the vehicle 1 stops, air heated by the cooling pipes 17 rises and is cooled by convection.
  • the opening space 19 is defined below the rows of the direct cooling-pipe group 18. Therefore, air is more likely to flow into the space below the direct cooling-pipe group 18 from the outside of the cooler 15, and hence cooling by the convection is also successfully performed. Further, cooling from the upper surface of the transformer tank 13 can also be performed.
  • the cooler 15 have a configuration in which most of the cooling pipes 17 are arranged on the upper surface side of the transformer tank 13.
  • the extending direction of the cooling pipes 17 may suitably be changed.
  • the direct cooling-pipe group 18 has the configuration in which the opening space 19 is defined and opened so as to be elongated in the Y direction with respect to the Z direction, the traveling wind is more likely to flow into the space defined between the direct cooling-pipe group 18 and the transformer tank 13, and in particular, the cooling performance of the cooler 15 is improved.
  • the inlet header 16a and the outlet header 16b are both installed on the transformer tank 13.
  • at least one of the inlet header 16a and the outlet header 16b may be arranged on the side of the transformer tank 13, that is, in the +Y direction or the -Y direction.
  • at least one of the first bent portion and the second bent portion of each of the cooling pipes 17 may be arranged on the side of the transformer tank 13.
  • the cooler having a configuration capable of cooling the refrigerant by heat exchange with air is provided on the upper surface of the transformer tank which is configured to accommodate the winding wire and store the refrigerant.
  • the cooler includes: the cooling-pipe mechanism, which is formed of the plurality of cooling pipes, and is arranged in the Z-direction from the upper surface of the transformer tank; the inlet header, which is configured to allow the refrigerant to flow into the cooling-pipe mechanism from the circulation pump side; and the outlet header, which is configured to allow the refrigerant having flowed through the cooling-pipe mechanism to flow out to the transformer tank side.
  • the cooling-pipe mechanism which is formed of the plurality of cooling pipes, and is arranged in the Z-direction from the upper surface of the transformer tank
  • the inlet header which is configured to allow the refrigerant to flow into the cooling-pipe mechanism from the circulation pump side
  • the outlet header which is configured to allow the refrigerant having flowed through the cooling-pipe mechanism to flow out to the transformer tank side.
  • cooling-pipe mechanism including the direct cooling-pipe group including a plurality of cooling pipes, which are arranged so as to allow the refrigerant to flow out from the inlet header and flow into the outlet header and are elongated in the Y direction and arrayed in a plurality of rows in the X direction.
  • the wind-guiding distance can be minimized, and the installation space for the traction transformer can be reduced.
  • description of the features which are the same as those of the first example which is not part of the present invention is omitted, and features which are different from those of the first example which is not part of the present invention are mainly described.
  • FIG. 10 is a perspective view for illustrating the cooler 15A in the first embodiment of the present invention.
  • the cooler 15A includes the inlet header 16a, the outlet header 16b, an intermediate header 20, an inlet-side cooling-pipe group 21a, and an outlet-side cooling-pipe group 21b.
  • the inlet header 16a is configured to allow refrigerant to flow thereinto from the circulation pump 14 side.
  • the outlet header 16b is configured to allow the refrigerant to flow out to the transformer tank side.
  • the intermediate header 20 is arranged between the inlet header 16a and the outlet header 16b.
  • the inlet-side cooling-pipe group 21a is arranged so as to allow the refrigerant to flow out from the inlet header 16a and flow into the intermediate header 20.
  • the outlet-side cooling-pipe group 21b is arranged so as to allow the refrigerant, which has once been gathered, to flow out from the intermediate header 20 and then flow into the outlet header 16b.
  • the cooling-pipe mechanism includes the inlet-side cooling-pipe group 21a connected to the inlet header 16a and the outlet-side cooling-pipe group 21b connected to the outlet header 16b.
  • the inlet header 16a, the inlet-side cooling-pipe group 21a, the intermediate header 20, the outlet-side cooling-pipe group 21b, and the outlet header 16b are connected in series.
  • the intermediate header 20 connecting the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b is configured to mix inside thereof the refrigerant having flowed into the intermediate header 20 from the inlet-side cooling-pipe group 21a, and allow the refrigerant to flow out to the outlet-side cooling-pipe group 21b while the refrigerant is re-distributed.
  • the inlet-side cooling-pipe group 21a includes a plurality of cooling pipes 17 arrayed in a plurality of rows in the X direction.
  • the outlet-side cooling-pipe group 21b includes a plurality of cooling pipes 17 arrayed in a plurality of rows in the X direction.
  • the inlet-side cooling-pipe group 21a is formed of the cooling pipes 17 arrayed in a plurality of rows at a constant pitch in the X direction.
  • the plurality of rows of the cooling pipes 17 each include six cooling pipes 17.
  • the six cooling pipes 17 are arranged on the Y-Z plane, have different sizes, and each have a U-shape protruding in the +Z direction.
  • the outlet-side cooling-pipe group 21b is formed of the cooling pipes 17 arrayed in a plurality of rows at a constant pitch in the X direction.
  • the plurality of rows of the cooling pipes 17 each include six cooling pipes 17.
  • the six cooling pipes 17 are arranged on the Y-Z plane, have different sizes, and each have a U-shape protruding in the +Z direction.
  • the inlet header 16a is connected to the circulation pump 14 side, that is, to the inlet-side pipe 12a.
  • the refrigerant having been increased in temperature due to heat received from, for example, the winding wire 11 flows into the inlet header 16a through the circulation pump 14.
  • the inlet header 16a has a shape elongated in the X direction.
  • the outlet header 16b is connected to the outlet-side pipe 12a to return the refrigerant, which has been decreased in temperature as compared to the refrigerant inside the inlet header 16a, to the transformer tank 13.
  • the outlet header 16b has a shape elongated in the X direction.
  • the intermediate header 20 is installed between the inlet header 16a and the outlet header 16b, and is arranged on the X-Y plane which is the same as the plane on which the inlet header 16a and the outlet header 16b are arranged.
  • the intermediate header 20 has a shape elongated in the X direction.
  • the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b are located on the upper surface side of the transformer tank 13.
  • the inlet-side cooling-pipe group 21a is arranged at the -Y direction end in the Y direction, and the outlet-side cooling-pipe group 21b is arranged at the +Y direction end in the Y direction. That is, for example, when it is assumed that the inlet-side cooling-pipe group 21a is arranged on the right side of the drawing sheet with respect to the X direction, the outlet-side cooling-pipe group 21b is arranged on the left side of the drawing sheet with respect to the X direction. It is preferred that the intermediate header 20 be located on the upper surface of the transformer tank 13.
  • the allowable height in the Z direction is about 0.3 m, and hence limitation on the height is strict.
  • a length of about 1 m in the Y direction and a length of about 2.5 m in the X direction can be secured. With this, the cooler 15A can be arranged with a relatively sufficient space.
  • the vehicle 1 requires a large amount of power at the time of acceleration during traveling, and a large amount of current flows through the winding wire 11 of the transformer 10. Therefore, the heat generation amount of the transformer 10 increases. Meanwhile, also when the vehicle is stopped, power is required for air conditioners and illumination devices. Thus, the transformer 10 generates heat even though the heat generation amount is not as large as that given during the traveling of the vehicle 1. Therefore, cooling of the transformer 10 is required not only during traveling of the vehicle but also when the vehicle is stopped.
  • the wind cannot flow into the cooler 15A. That is, in order to allow the cooler 15A to obtain high cooling performance during the traveling of the vehicle, it is required that a large number of cooling pipes 17 be arranged on the Y-Z cross section exposed to the traveling wind 5 during the traveling of the vehicle.
  • the space on the upper surface of the transformer tank 13 is a flat space which is elongated in the horizontal direction, that is, elongated in the X direction and the Y direction. Therefore, as in the case of the cooler 15 illustrated in FIG. 9 , when the large opening space 19 is defined at the center portion of the cooler 15, there is a possibility that the cooling efficiency per unit volume of the cooler cannot be improved.
  • the intermediate header 20 is used to form the cooler 15A with the inlet-side cooling-pipe group 21a provided so as to allow the refrigerant to flow into the intermediate header 20 from the inlet header 16a and the outlet-side cooling-pipe group 21b provided so as to allow the refrigerant to flow out from the intermediate header 20 and flow into the outlet header 16b.
  • the cooler 15A in the flat space elongated in the horizontal direction on the upper surface of the transformer tank 13, a large number of cooling pipes 17 can be arrayed on a passage plane of the traveling wind 5, that is, the Y-Z plane. As a result, the cooler having high heat-rejection performance per unit volume can be obtained at low cost.
  • the cooler 15 illustrated in FIG. 9 is arranged so as to fill the flat space elongated in the horizontal direction on the upper surface of the transformer tank 13, the pipe length of the cooling pipes 17 in the Y direction becomes larger.
  • the temperature of the refrigerant flowing inside the cooling pipes 17 is high.
  • the traveling wind 5 is less likely to flow thereinto.
  • the thermal flux with the outside air is small. Therefore, even in a periphery of the outlet header 16b, the temperature of the refrigerant does not significantly decrease from the temperature in a periphery of the inlet header 16a.
  • the intermediate header 20 is arranged between the refrigerant flow passages of the inlet header 16a and the outlet header 16b.
  • the refrigerant flows into the plurality of cooling pipes 17 from the inlet header 16a, and the refrigerant having flowed through the region 31 in which the heat rejection has proceeded due to exposure to the traveling wind 5 and the refrigerant having flowed through the region 32a that is less decreased in temperature without inflow of the traveling wind 5 can be mixed once in the intermediate header 20.
  • the temperature of the refrigerant flowing through the region 31b exposed to the traveling wind 5 flowing at high flow velocity can be maintained higher as compared to the case in which the intermediate header 20 is not provided. Therefore, as compared to the case in which the intermediate header 20 is not provided, an overall heat rejection amount of the cooler can be set higher.
  • FIG. 11 is a top sectional view of the intermediate header 20 in the first embodiment of the present invention.
  • a flow straightening plate 22 is arranged in the X direction in the intermediate header 20 so as to partition the inlet-side cooling-pipe group 21a connected to the inlet header 16a and the outlet-side cooling-pipe group 21b connected to the outlet header 16b.
  • a +X direction end of the flow straightening plate 22 is connected to a header end surface of the intermediate header 20, and a -X direction end of the flow straightening plate 22 is not connected to a header end surface of the intermediate header 20.
  • a flow passage cross section of each of the cooling pipes 17 has a flat shape with a large diameter in the X direction.
  • pressure loss caused when the traveling wind 5 passes through the cooler 15A can be reduced.
  • the refrigerant flowing into a region 33a of the intermediate header 20 from the inlet header 16a through the inlet-side cooling-pipe group 21a is exposed to the traveling wind 5 during traveling of the vehicle. Therefore, the temperature of the refrigerant is lower than the temperature of the refrigerant flowing into a region 33b in which the heat exchange with the traveling wind 5 does not proceed.
  • the refrigerant having been delivered from the inlet header 16a is mixed once, and hence equalization of the temperature of the refrigerant is promoted in the region 33c.
  • the mode of the flow straightening plate 22 is not limited to this. Any other mode may be employed as long as the equalization of the temperature of the refrigerant can be promoted through mixing of the refrigerant in the intermediate header 20. For example, even in the mode in which the -X direction end of the flow straightening plate 22 is connected to the header end surface and in which the +X direction end of the flow straightening plate 22 is not connected to the header end surface, the same effect as that of the mode described above can be attained.
  • the intermediate header 20 includes the flow straightening plate 22 configured to promote the equalization of the temperature of the refrigerant in the intermediate header 20.
  • the cooling-pipe mechanism of the cooler includes the inlet-side cooling-pipe group connected to the inlet header and the outlet-side cooling-pipe group connected to the outlet header.
  • the inlet-side cooling-pipe group and the outlet-side cooling-pipe group are connected through intermediation of the intermediate header.
  • a thin cooler including the plurality of cooling pipes arrayed in a plurality of rows in a distributed manner can be provided at low cost. Therefore, as compared to the first example which is not part of the present invention, the cooler can be more easily arranged in a narrow space on the upper surface of the transformer tank.
  • the cooling-pipe mechanism of the cooler 15A may include the direct cooling-pipe group which is directly connected from the inlet header 16a to the outlet header 16b without the intermediate header 20.
  • the flow straightening plate 22 is provided inside the intermediate header 20, and hence the effect of equalizing the temperature of the refrigerant is excellent.
  • the effect of equalization can be attained to some extent even without the flow straightening plate 22.
  • a structure for promoting mixing of the refrigerant such as a protrusion-and-recess structure or fins which may cause a turbulent flow in the refrigerant inside the intermediate header 20.
  • inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b may be connected to each other through intermediation of a plurality of intermediate headers 20 arranged between the inlet header 16a and the outlet header 16b.
  • the transformer 10 including a cooler 15B having a configuration different from that of the cooler 15 in the first example which is not part of the present invention and that of the cooler 15A in the first embodiment of the present invention.
  • description of the features which are the same as those of the first example which is not part of the present invention and the first embodiment of the present invention is omitted, and features which are different from those of the first example which is not part of the present invention and the first embodiment of the present invention are mainly described.
  • FIG. 12 is a perspective view for illustrating the cooler 15B in the second example which is not part of the present invention.
  • FIG. 13 is a rear perspective view of the cooler 15B of FIG. 12 .
  • the cooler 15B includes the inlet header 16a, the outlet header 16b, an upstream-side intermediate-header portion, a downstream-side intermediate-header portion, the inlet-side cooling-pipe group 21a, the outlet-side cooling-pipe group 21b, and a direct cooling-pipe group 24.
  • the inlet header 16a is configured to allow the refrigerant to flow thereinto from the circulation pump 14 side.
  • the outlet header 16b is configured to allow the refrigerant to flow out to the transformer tank side.
  • the upstream-side intermediate-header portion and the downstream-side intermediate-header portion are arrayed in the X direction between the inlet header 16a and the outlet header 16b.
  • the inlet-side cooling-pipe group 21a is arranged so as to allow the refrigerant to flow out from the inlet header 16a and flow into each of the upstream-side intermediate-header portion and the downstream-side intermediate-header portion.
  • the outlet-side cooling-pipe group 21b is arranged so as to allow the refrigerant to flow out from each of the upstream-side intermediate-header portion and the downstream-side intermediate-header portion and flow into the outlet header 16b.
  • the direct cooling-pipe group 24 is arranged so as to allow the refrigerant to flow out from the inlet header 16a and flow into the outlet header 16b.
  • the intermediate header in the second example which is not part of the present invention includes the upstream-side intermediate-header portion and the downstream-side intermediate-header portion which are arrayed in the X direction between the inlet header 16a and the outlet header 16b.
  • the terms "upstream” and "downstream" of the upstream-side intermediate-header portion and the downstream-side intermediate-header portion correspond to upstream and downstream in the traveling direction, and do not correspond to upstream and downstream of the flow of the refrigerant.
  • the inlet-side cooling-pipe group 21a in the second example which is not part of the present invention includes an upstream-side relay cooling-pipe group connected to the upstream-side intermediate-header portion and a downstream-side relay cooling-pipe group connected to the downstream-side intermediate-header portion.
  • Those two relay cooling-pipe groups forming the inlet-side cooling-pipe group 21a are each formed of the cooling pipes 17 arrayed in a plurality of rows at a constant pitch in the X direction.
  • the plurality of rows of the cooling pipes 17 each include six cooling pipes 17.
  • the six cooling pipes 17 are arranged on the Y-Z plane, have different sizes, and each have a U-shape protruding in the +Z direction.
  • a flow passage cross section of each of the cooling pipes 17 forming the inlet-side cooling-pipe group 21a has a flat shape having a diameter which is larger in the X direction.
  • the outlet-side cooling-pipe group 21b includes an upstream-side relay cooling-pipe group connected to the upstream-side intermediate-header portion and a downstream-side relay cooling-pipe group connected to the downstream-side intermediate-header portion.
  • Those two relay cooling-pipe groups forming the outlet-side cooling-pipe group 21b are each formed of the cooling pipes 17 arrayed in a plurality of rows at a constant pitch in the X direction.
  • the plurality of rows of the cooling pipes 17 each include six cooling pipes 17.
  • the six cooling pipes 17 are arranged on the Y-Z plane, have different sizes, and each have a U-shape protruding in the +Z direction.
  • a flow passage cross section of each of the cooling pipes 17 forming the inlet-side cooling-pipe group 21b has a flat shape having a diameter which is larger in the X direction.
  • the inlet-side cooling-pipe group 21a is arranged at the -Y direction end in the Y direction, and the outlet-side cooling-pipe group 21b is arranged at the +Y direction end in the Y direction.
  • the direct cooling-pipe group 24 is formed of the plurality of cooling pipes 17, which are elongated in the Y direction and arrayed in a plurality of rows in the X direction.
  • the direct cooling-pipe group 24 connects the inlet header 16a and the outlet header 16b to each other.
  • the direct cooling-pipe group 24 is formed of the cooling pipes 17 arrayed in a plurality of rows at a constant pitch along the X direction.
  • the plurality of rows of the cooling pipes 17 each include six cooling pipes 17.
  • the six cooling pipes 17 are arranged on the Y-Z plane, have different sizes, and each have a U-shape protruding in the +Z direction.
  • a flow passage cross section of each of the cooling pipes 17 forming the direct cooling-pipe group 24 has a flat shape having a diameter which is larger in the X direction.
  • the upstream-side intermediate-header portion is arranged at the +X direction end, and the downstream-side intermediate-header portion is arranged at the -X direction end.
  • the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b are arranged at each of the +X direction end and the -X direction end.
  • the direct cooling-pipe group 24 is arranged between the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b arranged at the X direction end, and the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b arranged at the -X direction end.
  • the upstream-side intermediate-header portion has a first space 25a for allowing the refrigerant to flow thereinto from the inlet-side cooling-pipe group 21a and a second space 25b for allowing the refrigerant to flow out to the outlet-side cooling-pipe group 21b.
  • the downstream-side intermediate-header portion has a first space 26a for allowing the refrigerant to flow thereinto from the inlet-side cooling-pipe group 21a and a second space 26b for allowing the refrigerant to flow out to the outlet-side cooling-pipe group 21b.
  • the upstream-side intermediate-header portion includes a header 25 and a partition plate 27.
  • the partition plate 27 is configured to partition the inside of the header 25 into the first space 25a for allowing the refrigerant to flow thereinto from the inlet-side cooling-pipe group 21a and the second space 25b for allowing the refrigerant to flow out to the outlet-side cooling-pipe group 21b.
  • the downstream-side intermediate-header portion includes a header 26 and the partition plate 27.
  • the partition plate 27 is configured to partition the inside of the header 26 into the first space 26a for allowing the refrigerant to flow thereinto from the inlet-side cooling-pipe group 21a and the second space 26b for allowing the refrigerant to flow out to the outlet-side cooling-pipe group 21b.
  • the cooling pipes 17 forming the inlet-side cooling-pipe group 21a the plurality of cooling pipes 17 located at the +X direction end are connected to the first space 25a of the upstream-side intermediate-header portion, and the plurality of remaining cooling pipes 17 located at the -X direction end are connected to the first space 26a of the downstream-side intermediate-header portion.
  • the plurality of cooling pipes 17 located at the +X direction end are connected to the second space 25b of the upstream-side intermediate-header portion, and the plurality of remaining cooling pipes 17 located at the -X direction end are connected to the second space 26b of the downstream-side intermediate-header portion.
  • the cooler 15B further includes a first auxiliary pipe 28 and a second auxiliary pipe 29.
  • the first auxiliary pipe 28 serves as a first flow passage for allowing the refrigerant to flow from the first space 25a of the upstream-side intermediate-header portion to the second space 26b of the downstream-side intermediate-header portion.
  • the second auxiliary pipe 29 serves as a second flow passage for allowing the refrigerant to flow from the first space 26a of the downstream-side intermediate-header portion to the second space 25b of the upstream-side intermediate-header portion.
  • the partition plate 27 is arranged in each of the header 25 and the header 26 so as to partition in the Y direction and be elongated in the X direction.
  • the partition plate 27 arranged in the header 25 partitions the space inside the header 25 into the first space 25a and the second space 25b.
  • the partition plate 27 arranged in the header 26 partitions the space inside the header 26 into the first space 26a and the second space 26b.
  • the first auxiliary pipe 28 connects the first space 25a and the second space 26b to each other.
  • the second auxiliary pipe 28 connects the first space 26a and the second space 25b to each other.
  • the refrigerant having flowed into the inlet-side cooling-pipe group 21a arranged at the +X direction end from the inlet header 16a flows into the first space 25a of the header 25.
  • the refrigerant having flowed into the first space 25a flows into the second space 26b of the header 26 through the first auxiliary pipe 28.
  • the refrigerant having flowed into the second space 26b flows into the outlet header 16b through the outlet-side cooling-pipe group 21b arranged at the - X direction end.
  • the refrigerant having flowed into the inlet-side cooling-pipe group 21a arranged at the -X direction end from the inlet header 16a flows into the first space 26a of the header 26.
  • the refrigerant having flowed into the first space 26a flows into the second space 25b of the header 25 through the second auxiliary pipe 29.
  • the refrigerant having flowed into the second space 25b flows into the outlet header 16b through the outlet-side cooling-pipe group 21b arranged at the +X direction end.
  • the cooler 15B has a configuration in which only the cooling pipes 17 which are arranged at the X direction end and highly contribute to the heat rejection during traveling of the vehicle are densely arranged on the Y-Z plane. With such a configuration, as illustrated in FIG. 13 , the opening space 19 is defined at the center portion of the cooler 15B.
  • the cooling pipes 17 are arrayed in a plurality of stages in the X direction, the increase in pressure loss of the wind passage system of the cooler for the traveling wind can be suppressed. Moreover, the traveling wind can spread over the entirety of the cooler. With this, the heat-rejection performance of the cooler can be maximally brought out.
  • the cooler 15B has the following configuration. That is, the refrigerant flow passage is provided between the first space 25a and the second space 26b through use of the first auxiliary pipe 28, and the refrigerant flow passage is provided between the first space 26a and the second space 25b through use of the second auxiliary pipe 29.
  • the refrigerant having a high temperature can be exposed to the traveling wind flowing upstream of the flow field, which has not yet received heat from the refrigerant and has not been increased in temperature.
  • the thermal flux from the refrigerant to the outside air can be increased, and hence high heat-rejection performance can be obtained in the cooler 15B installed in the limited space.
  • the upstream-side intermediate-header portion and the downstream-side intermediate-header portion each include a first header and a second header arrayed in the Y direction.
  • the first auxiliary pipe 28 allows the refrigerant to flow from the first header of the upstream-side intermediate-header portion to the second header of the downstream-side intermediate-header portion.
  • the second auxiliary pipe 29 allows the refrigerant to flow from the first header of the downstream-side intermediate-header portion to the second header of the upstream-side intermediate-header portion.
  • the cooler 15B includes, in addition to the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b, the direct coupling-pipe group 24 which is arranged so as to allow the refrigerant to flow out from the inlet header 16a and directly flow into the outlet header 16b.
  • all of the cooling pipe groups of the cooler 15B may be formed of only the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b.
  • the upstream-side intermediate-header portion and the downstream-side intermediate-header portion may form an integrated structure, and flow passages corresponding to the first auxiliary pipe 28 and the second auxiliary pipe 29 may be provided inside the structure.
  • the cooling-pipe mechanism of the cooler includes the inlet-side cooling-pipe group connected to the inlet header and the outlet-side cooling-pipe group connected to the outlet header.
  • the inlet-side cooling-pipe group connected to the inlet header includes the upstream-side relay cooling-pipe group connected to the upstream-side intermediate-header portion and the downstream-side relay cooling-pipe group connected to the downstream-side intermediate-header portion.
  • the outlet-side cooling-pipe group connected to the outlet header includes the upstream-side relay cooling-pipe group connected to the upstream-side intermediate-header portion and the downstream-side relay cooling-pipe group connected to the downstream-side intermediate-header portion.
  • the same effect as that of the first example which is not part of the present invention and the first embodiment of the present invention can be attained. Further, through the arrangement of the upstream-side intermediate-header portion at the +X direction end and the arrangement of the downstream-side intermediate-header portion at the -X direction end, as compared to the first example which is not part of the present invention and the first embodiment of the present invention, the heat-rejection performance of the cooler can be more maximally brought out.
  • a diameter in the X direction of each of the cooling pipes 17 forming the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b is set larger than a diameter in the X direction of each of the cooling pipes 17 forming the direct cooling-pipe group 24.
  • description of the features which are the same as those of the previous examples which are not part of the present invention and the first embodiment of the present invention is omitted, and features which are different from are mainly described.
  • FIG. 14 is a sectional view for illustrating the inlet-side cooling-pipe group 21a, the outlet-side cooling-pipe group 21b, and the direct cooling-pipe group 24 in the third example which is not part of the present invention.
  • the cooling pipes 17 forming each of the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b are equal in diameter in the Z direction but larger in diameter in the X direction with respect to the cooling pipes 17 forming the direct cooling-pipe group 24.
  • the flow passage for the refrigerant flowing from the inlet header 16a to the outlet header 16b through the header 25 and the header 26 has more bending portions in the flow passage as compared to the flow passage for the refrigerant directly flowing from the inlet header 16a to the outlet header 16b, with the result that the pressure loss increases.
  • a flow-passage sectional area of the cooling pipe having the U-shape is sensitive with respect to the pressure loss in the refrigerant flow passage. Therefore, when the flow-passage sectional area of each of the cooling pipes 17 forming the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b is set larger than the flow-passage sectional area of each of the cooling pipes 17 forming the direct cooling-pipe group 24, the pressure loss can be evenly set for the refrigerant flow passages. However, when the flow passage cross section for the traveling wind 5 is set narrow, the traveling wind 5 becomes less likely to flow into the cooler 15B.
  • the diameter in the X direction of each of the cooling pipes 17 forming the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b is set larger than the diameter in the X direction of each of the cooling pipes 17 forming the direct cooling-pipe group 24.
  • the increase in pressure loss in the refrigerant flow passages can be suppressed by setting the flow-passage sectional area of each of the first auxiliary pipe 28 and the second auxiliary pipe 29 to be larger than the flow-passage sectional area of each of the cooling pipes 17 forming the inlet-side cooling-pipe group 21a and the outlet-side cooling-pipe group 21b. As a result, degradation in flow rate balance of the refrigerant flowing through the cooling pipes 17 can be prevented.
  • the diameter in the X direction of each of the cooling pipes forming the inlet-side cooling-pipe group and the outlet-side cooling-pipe group is set larger than the diameter in the X direction of each of the cooling pipes forming the cooling-pipe group.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Transformer Cooling (AREA)

Claims (5)

  1. Traktionstransformator (10) mit einer Dickenrichtung, die einer Z-Richtung entspricht, einer Breitenrichtung, die einer Y-Richtung entspricht, und einer Längenrichtung, die einer X-Richtung entspricht, die geeignet ist zur Installation auf einem Dach (2) von einem Fahrzeug (1) und der dazu ausgelegt ist, mit der X-Richtung ausgefluchtet parallel zu der Fahrtrichtung des Fahrzeugs montiert zu werden, wobei die Anordnung Folgendes aufweist:
    - eine Hauptleitung (12), die eine Zirkulationspassage für ein Kühlmittel bildet;
    - einen Transformatortank (13), der in der Zirkulationspassage angeordnet ist und dazu ausgelegt ist, einen Wicklungsdraht (11) unterzubringen und das Kühlmittel zu speichern;
    - eine Umwälzpumpe (14), die in der Zirkulationspassage angeordnet und die dazu ausgelegt ist, das Kühlmittel in der Zirkulationspassage zirkulieren zu lassen; und
    - einen Kühler (15A), der in der Zirkulationspassage und auf einer oberen Oberfläche des Transformatortanks (13) angeordnet ist und dazu ausgelegt ist, das Kühlmittel durch einen Wärmeaustausch mit Luft zu kühlen, wobei die obere Oberfläche eine Oberfläche ist, die senkrecht zu der Z-Richtung ist,
    wobei der Kühler (15A) einen Kühlleitungsmechanismus aufweist, der zumindest eine Kühlleitungsgruppe aufweist, von denen jede aus einer Vielzahl von Kühlleitungen (17) gebildet ist, und in der Z-Richtung von der oberen Oberfläche des Transformatortanks (13) aus angeordnet ist,
    wobei der Kühlleitungsmechanismus zw ischen einen Einlass-Verteiler (16a) und einen Auslass-Verteiler (16b) geschaltet ist, wobei der Einlass-Verteiler (16a) mit der Umwälzpumpe (14) verbunden ist und dazu ausgelegt ist, das Kühlmittel von der Umwälzpumpe (14) zu erhalten und das Kühlmittel an den Kühlleitungsmechanismus zu verteilen, und wobei der Auslass-Verteiler (16b) derart angeschlossen ist, dass er das Kühlmittel sammelt, das durch den Kühlleitungsmechanismus geflossen ist, und das Kühlmittel zu dem Transformatortank (13) zurückführt,
    wobei die mindestens eine Kühlleitungsgruppe Folgendes aufweist:
    - eine einlassseitige Kühlleitungsgruppe (21a), die mit dem Einlass-Verteiler (16a) verbunden ist; und
    - eine auslassseitige Kühlleitungsgruppe (21b), die mit dem Auslass-Verteiler (16b) verbunden ist,
    dadurch gekennzeichnet,
    dass der Kühler (15A) ferner einen Zwischen-Verteiler (20) aufweist, der die einlassseitige Kühlleitungsgruppe (21a) und die auslassseitige Kühlleitungsgruppe (21b) miteinander verbindet,
    wobei der Zwischen-Verteiler (20) eine Strömungsausgleichsplatte (22) aufweist, die in der X-Richtung angeordnet ist, um die einlassseitige Kühlleitungsgruppe (21a) und die auslassseitige Kühlleitungsgruppe (21b) zu trennen, und dazu ausgebildet ist, einen Temperaturausgleich des Kühlmittels im Inneren des Zwischen-Verteilers (20) zu unterstützen,
    wobei die Strömungsausgleichsplatte (22) ein erstes Ende in der X-Richtung und ein zweites Ende in der X-Richtung aufweist, und wobei der Zwischen-Verteiler eine erste Endoberfläche in der X-Richtung und eine zweite Endoberfläche in der X-Richtung aufweist, und
    wobei entweder:
    das erste Ende der Strömungsausgleichsplatte (22) in der X-Richtung mit der ersten Endoberfläche des Zwischen-Verteilers (20) in der X-Richtung verbunden ist und ein Spalt zwischen dem zweiten Ende der Strömungsausgleichsplatte (22) in der X-Richtung und der zweiten Endoberfläche des Zwischen-Verteilers (20) in der X-Richtung ausgebildet ist,
    oder
    das zweite Ende der Strömungsausgleichsplatte (22) in der X-Richtung mit der zweiten Endoberfläche des Zwischen-Verteilers (20) in der X-Richtung verbunden ist und ein Spalt zwischen dem ersten Ende der Strömungsausgleichsplatte (22) in der X-Richtung und der ersten Endoberfläche des Zwischen-Verteilers in der X-Richtung ausgebildet ist, oder
    beide, also das erste Ende und das zweite Ende der Strömungsausgleichsplatte (22) in der X-Richtung jeweils mit einer von der ersten Endoberfläche und der zweiten Endoberfläche des Zwischen-Verteilers (20) in der X-Richtung verbunden ist und ein Spalt in einem Zwischenbereich der Strömungsausgleichsplatte ausgebildet ist.
  2. Traktionstransformator nach Anspruch 1,
    wobei die mindestens eine Kühlleitungsgruppe eine direkte Kühlleitungsgruppe aufweist, welche eine erste Vielzahl von Kühlleitungen (17) als eine Vielzahl von Kühlleitungen (17) aufweist, die langgestreckt in der Y-Richtung angeordnet sind und in einer ersten Vielzahl von Reihen in der X-Richtung angeordnet ist und welche den Einlass-Verteiler (16a) und den Auslass-Verteiler (16b) miteinander verbindet.
  3. Traktionstransformator nach Anspruch 1 oder 2,
    wobei der Einlass-Verteiler (16a), der Auslass-Verteiler (16b) und der Zwischen-Verteiler (20) in derselben X-Y-Ebene angeordnet sind.
  4. Traktionstransformator nach einem der Ansprüche 1 bis 3,
    wobei jede von den Kühlleitungen (17) einen Strömungspassagen-Querschnitt besitzt, wobei der Strömungspassagen-Querschnitt eine flache Gestalt besitzt, die einen größeren Querschnitts-Durchmesser in der X-Richtung als in jeder anderen Richtung besitzt.
  5. Traktionstransformator nach einem der Ansprüche 1 bis 4,
    wobei jede der Kühlleitungen eine U-Form aufweist.
EP16916188.2A 2016-09-13 2016-09-13 Transformator für fahrzeug Active EP3514812B1 (de)

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EP3514812B1 true EP3514812B1 (de) 2022-09-21

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EP3703992B1 (de) * 2017-10-30 2024-07-31 Hitachi Energy Ltd Kühlsystem für eine elektrische energieumwandlungsvorrichtung eines schienenfahrzeugs
DE112021008031T5 (de) * 2021-07-27 2024-05-08 Mitsubishi Electric Corporation Bordseitige Vorrichtung
CN114843081A (zh) * 2022-05-31 2022-08-02 中车株洲电机有限公司 集成式牵引变压器总成
CN114843079A (zh) * 2022-05-31 2022-08-02 中车株洲电机有限公司 轨道交通车辆牵引变压器总成
JP7509336B1 (ja) 2023-12-11 2024-07-02 三菱電機株式会社 車両用変圧器

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JPS5012771Y1 (de) * 1970-12-03 1975-04-19
JPS5412817U (de) * 1977-06-29 1979-01-27
JPS5660765A (en) * 1979-10-24 1981-05-25 Mitsubishi Electric Corp Cooler for electrical machinery and apparatus for car
JPS5984816U (ja) 1982-11-29 1984-06-08 三菱電機株式会社 冷却器
JP2619707B2 (ja) * 1988-11-26 1997-06-11 三菱電機株式会社 放熱装置
JPH03158666A (ja) * 1989-11-15 1991-07-08 Showa Alum Corp エバポレータ
JP4089567B2 (ja) * 2003-09-16 2008-05-28 株式会社デンソー 冷却用熱交換器モジュール
JP2007273777A (ja) 2006-03-31 2007-10-18 Toshiba Corp 車両用変圧器の冷却装置
JP2009124038A (ja) * 2007-11-16 2009-06-04 Toyo Electric Mfg Co Ltd 屋根置型電気車制御装置用半導体冷却装置
JP2011230655A (ja) * 2010-04-28 2011-11-17 Sanden Corp 車室内熱交換器
JP5946651B2 (ja) * 2012-02-28 2016-07-06 住友精密工業株式会社 熱交換器
JP5805354B1 (ja) * 2014-12-26 2015-11-04 三菱電機株式会社 車両用変圧器
JP6494384B2 (ja) * 2015-04-09 2019-04-03 三菱電機株式会社 車両用変圧器

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JP6180684B1 (ja) 2017-08-16
WO2018051403A1 (ja) 2018-03-22
EP3514812A4 (de) 2019-09-04
EP3514812A1 (de) 2019-07-24

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