WO2012116727A1 - Unité de refroidissement - Google Patents

Unité de refroidissement Download PDF

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Publication number
WO2012116727A1
WO2012116727A1 PCT/EP2011/052941 EP2011052941W WO2012116727A1 WO 2012116727 A1 WO2012116727 A1 WO 2012116727A1 EP 2011052941 W EP2011052941 W EP 2011052941W WO 2012116727 A1 WO2012116727 A1 WO 2012116727A1
Authority
WO
WIPO (PCT)
Prior art keywords
fan
heat exchanger
air
refrigerator according
fan units
Prior art date
Application number
PCT/EP2011/052941
Other languages
German (de)
English (en)
Inventor
Martin Doerrich
Dirk Hemann
Michael Nicolai
Jens Satzer
Daniel THEIS
Original Assignee
Rittal Gmbh & Co. Kg
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 Rittal Gmbh & Co. Kg filed Critical Rittal Gmbh & Co. Kg
Priority to PCT/EP2011/052941 priority Critical patent/WO2012116727A1/fr
Publication of WO2012116727A1 publication Critical patent/WO2012116727A1/fr

Links

Classifications

    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
    • H05K7/20718—Forced ventilation of a gaseous coolant
    • H05K7/20745—Forced ventilation of a gaseous coolant within rooms for removing heat from cabinets, e.g. by air conditioning device

Definitions

  • the invention relates to a cooling device with a receiving area in which a heat exchanger and at least one fan unit are arranged.
  • a known from WO 2009/141610 A1 cooling device is used for cooling of electronic components that are housed in racks or cabinets.
  • the refrigerator may be integrated in a series of racks or cabinets, which delimits a cold aisle in relation to a warm aisle in a data center.
  • the cooling unit takes in heated air from the aisle, cools it and then releases it into the cold aisle again.
  • Another construction variant is characterized in that the cooling device is mounted laterally on a control cabinet, as shown in DE 10 2006 051 904 A1.
  • This is a closed air circulation system through the cabinet and the Cooling device formed. Accordingly, air is sucked from the cabinet, passed through the refrigerator and then the cooled air is returned to the cabinet.
  • three fan units are arranged one above the other in a frame.
  • the frame is composed of twelve frame profiles, each four horizontal frame profiles form a floor and a cover frame.
  • the floor is connected to the deck frame via four vertical frame profiles.
  • one, two or three fan units can be integrated in the receiving space of the cooling unit.
  • the fan units can be easily retrofitted. They only have to be inserted through the front.
  • the frame on the front side, the two vertical frame profiles, the spaced apart parallel define an installation opening.
  • the data center increasingly demands that the building units installed in the data center provide high performance in a small space.
  • the building units installed in the data center provide high performance in a small space.
  • the object of the invention is achieved with a cooling device with a receiving space in which at least one heat exchanger and two or more superimposed fan units are held, wherein the heat exchanger is designed as an air-water heat exchanger, and transverse to the air flow direction a width of less than or equal to 300th mm, wherein all fan units generate an air flow over the heat exchanger and in each case a volume flow (V) in the range between 1, 000 m 3 / h and 1, 600 m 3 / h.
  • V volume flow
  • the receiving space thus forms an air flow channel, wherein the width is dimensionally dimensioned so that at the specified air flow rate an ideal flow profile is formed. In this way, there is a good efficiency and thus an energy-saving operation.
  • the width of the cooling unit is corresponding to half the grid unit of a common data center. Usually, a dimension of 600 mm is used as the raster unit. Thus, the cooling unit can be easily and space-saving kit-like integrated into a data center.
  • the fan units all operate via the heat exchanger, a redundancy is also created. If one of the fan units fails, the cooling capacity is still maintained by the other fan units.
  • water in the volume range between 80 and 160 l / min can be enforced by the heat exchanger.
  • the specified air flow rate of 1, 000 m 3 / h and 1 600 m 3 / h per fan unit the requirements for data centers can be met in particular and high power losses can be dissipated by secondary control cabinet units. In particular, no adverse interactions are caused by the simultaneous admission of a heat exchanger with multiple fan units at these high water flow rates.
  • each fan unit dissipates a power loss in the range between 8 and 12 kW.
  • the chiller width should be ⁇ 300 mm, the chiller height ⁇ 2200 mm and / or the chiller depth ⁇ 1400 mm.
  • an adequate At is made available for common server technologies.
  • a refrigerator may be characterized in that it uses a support structure with two mutually parallel spaced vertical frame profiles, wherein the vertical frame profiles front define a mounting hole, and that the fan units have a horizontally extending pave width which is greater than the clear distance between the vertical frame profiles.
  • the supporting structure provides a stable structural unit to which the heat exchanger and the fan units can be coupled.
  • the fan units can be mounted or dismounted via the front mounting hole in the installed state of the cooling unit. Because the mounting width is greater than the clear distance between the vertical frame profiles, a fan can be installed in the fan unit, which can promote large volume flows with maximum fan diameter. In addition, with such fans also high pressure differences can be overcome, so that for the purpose of high power output and corresponding heat exchanger can be used with high air resistance.
  • the fan unit is a radial fan or has a radial fan, which sucks the air in the direction of its axis of rotation and blows out in the radial direction
  • high pressure differences can be overcome with high air delivery volume.
  • the conveying blades of the radial fan are arranged such that they are curved counter to the direction of rotation of the radial fan. Then it can be achieved for the purpose of high air volume flow rate an increase in power output.
  • the required air flow rates in the range between 1 .000 m 3 / h and 1 .600 m 3 / h per fan unit can be achieved with such radial fans.
  • An alternative variant of the invention may be characterized in that the radial fan generates an air flow with a main flow direction through the heat exchanger, and that the axis of rotation of the radial fan at an angle is less than 90 ° to the main flow direction.
  • the radial fan is not ideally flown in the direction of its axis of rotation of the flow, but there is the particular advantage that large fan wheels can be installed in refrigerators with low housing width. As a result, a significant increase in performance can be achieved even with a non-ideal angle of attack.
  • the inclination of the radial fan also has the advantage that with a corresponding arrangement of a blowout the cooled air can be ejected through the front of the air conditioner, so that there is an ideal air flow path in the cold aisle.
  • the axis of rotation of the radial fan is set in the angular range between 0 ° and 90 ° to the main flow direction. In this angular range, only small flow losses result due to the non-ideal paraxial flow of the radial fan.
  • the radial fans are arranged folded against each other, so they suck on the one hand, the air also offset and above all the air ejected offset. This allows a particularly uniform action on the cold aisle with cooled air.
  • Figure 1 in perspective side view of a cooling device
  • FIG 2 is a schematic detail view of the cooling device according to Figure 1 in
  • Figure 3 is a perspective side view of a further embodiment variant of a cooling device.
  • FIG. 4 shows a schematic detail of the cooling device according to FIG. 3 in FIG.
  • Figure 1 shows a refrigerator with a frame 10, which surrounds a receiving space.
  • the frame 10 is composed of eight horizontal and four vertical frame profiles 1 1, 12, 13. In this case, two extending in the direction of the air conditioning depth horizontal frame profiles 1 1 and two extending in air conditioner width direction horizontal frame sections 12, a floor and a cover frame.
  • the floor frame is with the deck frame on the four vertical frame sections thirteenth connected in the corner regions of the frame 10.
  • the receiving space can be closed at the front with a cover 14.1 and at the back with a cover 14.2.
  • the covers 14.1, 14.2 are preferably hinged so that they form a door which makes the receiving space easily accessible.
  • a holder 15 is stably fixed to the bottom frame and the two vertical frame profiles 13.
  • the holder 15 carries a connection fitting 1 6, which forms both the flow and the return for a heat exchanger 20.
  • the heat exchanger 20 is cuboid and designed as an air-water heat exchanger. It is supported with a bottom-side and a top-side attachment 21 relative to the frame 10. In this case, the heat exchanger 20 extends in the vertical direction almost over the entire height of the frame 10 in the parallel to the horizontal frame profiles 12 extending frame frame width direction, the heat exchanger 20 also extends almost over the entire installation width of the receiving space.
  • the heat exchanger 20 is designed as a conventional air-water heat exchanger, which forms air ducts between heat exchanger plates.
  • the air ducts form a flow connection between the rear side of the heat exchanger 20 facing the cover 14,2 and the front side of the heat exchanger 20 facing the cover 14.1.
  • the heat exchanger 20 is accordingly perfused with air in the main flow direction HS (see FIG. 2).
  • a mist eliminator 30 connects. This is attached via brackets 31 to a condensate collector 40.
  • the condensate collector 40 is designed as a trough which extends in the depth direction both over the heat exchanger 20 and via the mist eliminator 30.
  • each fan receptacle has a bottom which forms a guide 65.
  • the floor is fixed by means of fasteners 64 to the vertical frame profiles 12 stable.
  • each fan mount a fan unit 60 can be used.
  • six fan mounts are arranged vertically one above the other and three fan mounts are occupied by three fan units 60. In this case, between the fan units 60 each have a fan tray is not occupied.
  • end walls 63 are used. On the one hand, these serve to seal off the air, on the other hand they support the adjacent guides 65 in the vertical direction against each other, resulting in a stable construction.
  • locking plates 68 are installed in the unused fan mounts.
  • FIG. 2 schematically illustrates a horizontal section through a fan unit 60 in the front region of the air conditioning unit.
  • an installation opening 18 is delimited between the two vertical frame profiles 13.
  • the fan units 60 are arranged in the assembled state behind the vertical frame profiles 13.
  • the installation width B of the fan units 60 running parallel to the front side in the horizontal direction is greater than the clear distance between the vertical frame profiles 13 in the horizontal direction.
  • the horizontal installation depth T of the fan unit 60 which runs perpendicular to the front side, is smaller than the clear distance between the vertical frame profiles 13. Accordingly, the fan unit 60 can be mounted in such a way that it is rotated by 90 ° relative to the installation situation shown in FIG. 2 through the installation opening 18 can be pushed through.
  • the insertion of the fan unit 60 succeeds easily on the guide 65. Behind the vertical frame profiles 13 then the fan unit 60th be rotated so that it reaches the installation state shown in Figure 2.
  • suitable fasteners can then fix the fan unit 60.
  • the fan units 60 comprise a radial fan 66, which draws in the air along its axis of rotation R and delivers it radially outward.
  • the flow direction is symbolized in Figure 2 with arrows.
  • the radial fan 66 is installed in the fan unit 60 in a fan housing 61, wherein the fan housing 61 has a blow-out opening 62 which is directed to the side of the refrigerator (in this case to the left side).
  • the radial fan 66 conveys air through the heat exchanger 20, thereby resulting in the main flow direction HS, which is directed from the back of the air conditioner to the front of the air conditioner out.
  • the sucked air is injected by means of the radial fan 66 laterally in a mounted control cabinet front.
  • the injected air flows through the control cabinet in the form of a horizontal air roll and accordingly leaves the control cabinet at the back. There, a corresponding air-conducting connection between the cabinet and the air conditioner is provided.
  • the air is then sucked in the direction of flow in front of the heat exchanger 20 back into the air conditioner and conveyed through the heat exchanger 20.
  • the air cools and is pulled through the mist eliminator 30. Any accumulating condensate is trapped in the droplet 30 and fed in the direction of gravity down to the condensate collector 40. Since the heat exchanger 20 is also set in the condensate collector 40, the condensate possibly arising on the heat exchanger 20 is caught in the condensate collector 40.
  • the cooling device can be equipped with one or more fan units 60.
  • the number of fan units 60 the cooling capacity of the refrigerator increases. A user can therefore depend on the desired performance data, the number of fan units 60 select. If the required cooling capacity increases, then additional fan units 60 can be added.
  • a redundancy can be covered by the number of fan units 60. For example, if three fan units 60 are sufficient for cooling, the user may insert a fourth fan unit 60 so that it receives an n + 1 redundancy.
  • the operating costs can be reduced by the number of fan units 60 used. For example, if three fan units 60 are sufficient to achieve the desired cooling capacity, then these fan units 60 run at maximum speed and thus with maximum energy consumption. For this reason, it is now possible to install further, for example, three further fan units 60 (ie up to a total of six fan units 60). As a result, the total air output per fan unit 60 decreases, whereby the energy consumption is reduced. This results in significant savings in operating costs and extended lifetimes.
  • the cooling device has six identical fan mounts, in which identical fan units 60 can be used in a modular manner.
  • the fan units 60 have an electrical connection, which enables activation of the fan units 60 in the plug-and-play method via the device software.
  • an electrical control circuit 50 is integrated in the receiving space of the cooling device. This is arranged downstream of the heat exchanger 20 in the flow direction. It is thus cooled by the heat exchanger 20 and there are no other design measures required for this. Furthermore, a spatial separation between the rear water-conducting area and the electrical system is achieved by this arrangement of the heat exchanger 20. In addition, the electric Control circuit 50 arranged for this purpose in the ceiling area of the frame 10.
  • the cooling device has a width parallel to the front side, ie transverse to the air flow direction through the heat exchanger 20 (main flow direction HS) less than or equal to 300 mm. This corresponds to half the standard unit in common data centers.
  • each fan unit 60 is designed such that it conveys an air volume flow in the range between 1 .000 m 3 and 1 .600 m 3 per hour.
  • the water throughput through the heat exchanger 20 should be in the range between 90 and 1 60 l / min in order to obtain a sufficiently uniform utilization of the heat exchanger 20 in the width direction in this narrow width. This is particularly necessary when the receiving space of the refrigerator has a volume in the range of 0.6 to 0.8 m 3 .
  • the cooling device shown in Figures 3 and 4 corresponds in the basic structure substantially to the cooling device according to Figures 1 and 2, so that below will be discussed only on the different design features and otherwise reference is made to the above statements.
  • each fan mount In the front region of the frame 10 six fan mounts are provided. These fan mounts are accessible with the front cover 14.1 open.
  • the two front vertical frame sections 13 and the front horizontal frame sections 1 1, 12 limit an installation opening through which one gets access to the fan mounts.
  • Each fan receptacle has a bottom which forms a guide 65.
  • the floor is fixed by means of fasteners 64 to the vertical frame profiles 12 stable.
  • a fan unit 60 can be used.
  • six fan mounts are arranged vertically one above the other and all fan mounts are each occupied by a fan unit 60. It is also conceivable that not all fan shots are occupied. In the area of the unoccupied fan mounts can then be used end walls, which prevent an air short circuit. Furthermore, the unused fan mounts are then bridged with the end walls and the occupied fan mounts are supported against each other. This results in a stable construction.
  • FIG. 4 schematically shows a horizontal section through a fan unit 60 in the front region of the air conditioning unit.
  • the fan units 60 are arranged in the assembled state behind the vertical frame profiles 13.
  • the fan units 60 are placed in the fan mounts on floors that serve as a guide 65.
  • the fan units 60 have a fan housing 61 with an exhaust opening 62.
  • a radial fan 66 is housed in the fan housing 61.
  • the radial fan 66 is preferably designed such that its conveying blades are curved counter to the direction of rotation of the radial fan 66, so it is a backward curved radial fan 66. This makes it possible to achieve a high power output for the purpose of high air volume delivery.
  • the radial fan 66 has almost the same size as the fan housing 61 in the horizontal direction.
  • the fan unit 60 has an installation depth T extending in the direction of the axis of rotation R of the radial fan 66 and a mounting width B extending in the horizontal direction perpendicular to the axis of rotation R.
  • the installation width B is chosen to be greater than the clear opening dimension of the installation opening 18 between the vertical frame profiles 13.
  • the installation width B can be selected to be larger than the velvet width of the cooling unit housing.
  • the radial fan 66 is turned by the heat exchanger 20 with respect to its axis of rotation R at an angle ⁇ ⁇ 90 ° to the main flow direction HS.
  • the blow-out opening 62 is offset relative to the front side by the installation dimension t and opposite to the side by the installation dimension b. This results between the front right vertical frame profile 13 and the right edge of the fan unit 60, a gap which, depending on its size, can be covered with a baffle to optimize the front blowout.
  • the fan unit 60 is particularly preferably employed and arranged such that it comes to rest with its outlet opening 62 in the space between the two vertical frame profiles 13. Then, an additional air baffle is not necessarily required, and the air can be deflected on the vertical frame profile 13 and output to the front.
  • the fan motor 67 which drives the radial fan 66, is held in a space-saving manner behind the left-hand vertical frame profile 13 and in front of the fan housing 61.
  • the axes of rotation R of the individual radial fans 66 are alternately set crosswise.
  • the uppermost radial fan 66 according to FIG. 1 blows its air to the left side
  • the radial fan 66 below it blows its air to the right side
  • the then adjoining radial fan 66 returns its air to the left side. Due to this mutual arrangement of the blowing openings 62, a particularly uniform application of a cold aisle is achieved.
  • the front-side installation opening 18 can be covered with the cover 14.1 designed as a door. This is designed as access protection perforated, so that creates an air-conductive connection to the environment. Furthermore, the rear cover 14.2 is formed perforated so that air to be cooled through this cover 14.2 can be sucked through.
  • the assembly of the individual fan units 60 succeeds easily. They are rotated so that they can be pushed with their installation depth T through the mounting hole 18 therethrough. A purposeful and simple assembly is achieved here by the fact that the fan units 60 can be pushed onto the guides 65. Behind the vertical frame profiles 13, the fan unit 60 can then optionally rotated in the intended position and then secured.
  • the radial fans 66 suck in cooling air through the perforated rear cover 14.2 from an aisle.
  • the air is then passed through the heat exchanger 20 and cooled by means of this.
  • the heat exchanger 20 is presently designed as an air-water heat exchanger, which has spaced-apart heat exchanger plates, between which air ducts are formed. After passing the heat exchanger 20, the air is drawn through the mist eliminator 30. Any accumulating condensate is trapped in the droplet 30 and fed in the direction of gravity down to the condensate collector 40. Since the heat exchanger 20 is also set in the condensate collector 40, the condensate possibly arising on the heat exchanger 20 is caught in the condensate collector 40.
  • the cooled air reaches the fan units 60 and is conveyed away by means of the radial fan 66 through the exhaust opening 62 and through ejected the perforated front cover 14.1.
  • the air then enters the cold aisle. It is available here for cooling purposes.
  • the cooling device can be equipped with one or more fan units 60. With the number of fan units 60, the cooling capacity of the refrigerator increases. A user can thus select the number of fan units 60 depending on the desired performance data. If the required cooling capacity increases, then additional fan units 60 can be added.
  • a redundancy can be covered by the number of fan units 60. For example, if three fan units 60 are sufficient for cooling, the user may insert a fourth fan unit 60 so that it receives an n + 1 redundancy.
  • the operating costs can be reduced by the number of fan units 60 used. For example, if three fan units 60 are sufficient to achieve the desired cooling capacity, then these fan units 60 run at maximum speed and thus with maximum energy consumption. For this reason, it is now possible to install further, for example, three further fan units 60 (ie up to a total of six fan units 60). As a result, the total air output per fan unit 60 decreases, whereby the energy consumption is reduced. This results in significant savings in operating costs and extended lifetimes.
  • the cooling device has six identical fan mounts, in which identical fan units 60 can be used in a modular manner.
  • the fan units 60 have an electrical connection, which enables activation of the fan units 60 in the plug-and-play method via the device software. As FIG.
  • an electrical control circuit 50 is integrated in the receiving space of the cooling device. This is arranged downstream of the heat exchanger 20 in the flow direction. It is thus cooled by the heat exchanger 20 and there are no other design measures required for this. Furthermore, a spatial separation between the rear water-conducting area and the electrical system is achieved by this arrangement of the heat exchanger 20. In addition, the electrical control circuit 50 is arranged for this purpose in the ceiling region of the frame 10.
  • the cooling device has a width parallel to the front side, ie transverse to the air flow direction through the heat exchanger 20 (main flow direction HS) less than or equal to 300 mm. This corresponds to half the standard unit in common data centers.
  • each fan unit 60 is designed such that it conveys an air volume flow in the range between 1 .000 m 3 and 1 .600 m 3 per hour.
  • the water throughput through the heat exchanger 20 should be in the range between 90 and 1 60 l / min in order to obtain a sufficiently uniform utilization of the heat exchanger 20 in the width direction in this narrow width. This is particularly necessary when the receiving space of the refrigerator has a volume in the range of 0.6 to 0.8 m 3 .

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  • Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

L'invention concerne une unité de refroidissement comprenant un logement dans lequel sont placés au moins un échangeur de chaleur et au moins deux blocs ventilateurs superposés, l'échangeur de chaleur étant un échangeur air-eau, et présentant une largeur totale inférieure ou égale à 300 mm perpendiculairement à la direction du flux d'air, tous les blocs ventilateurs produisant un flux d'air au dessus de l'échangeur de chaleur et transférant chacun un débit volumique d'air compris dans une plage de 1000 m3/h à 1600 m3/h. De par sa puissance de refroidissement et ses dimensions, une telle unité de refroidissement se prête idéalement à une application dans un centre de traitement de l'information.
PCT/EP2011/052941 2011-02-28 2011-02-28 Unité de refroidissement WO2012116727A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2011/052941 WO2012116727A1 (fr) 2011-02-28 2011-02-28 Unité de refroidissement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2011/052941 WO2012116727A1 (fr) 2011-02-28 2011-02-28 Unité de refroidissement

Publications (1)

Publication Number Publication Date
WO2012116727A1 true WO2012116727A1 (fr) 2012-09-07

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ID=44625288

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/052941 WO2012116727A1 (fr) 2011-02-28 2011-02-28 Unité de refroidissement

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Country Link
WO (1) WO2012116727A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015215535A1 (de) * 2015-08-14 2017-02-16 SCHäFER WERKE GMBH Spritzschutz für einen Wärmetauscher in einem Schrank für elektronische Komponenten
DE102016107531B3 (de) * 2016-04-22 2017-07-13 Rittal Gmbh & Co. Kg Schaltschrankanordnung mit einem in einem Schaltschrankgehäuse aufgenommenen Kühlgerät
DE102016201723A1 (de) * 2016-02-04 2017-08-10 SCHäFER WERKE GMBH Sidecooler mit einem Wärmetauscher zur Anordnung neben einem Schrank für elektronische Komponenten

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060067047A1 (en) * 2004-09-30 2006-03-30 Pfahnl Andreas C Modular liquid cooling of electronic assemblies
DE102006051904A1 (de) 2006-11-03 2008-05-15 Rittal Gmbh & Co. Kg Geräteanordnung mit einem Schaltschrank und einem Kühlgerät
WO2009141610A1 (fr) 2008-05-20 2009-11-26 Semper Holdings Limited Unité de refroidissement montée dans une baie

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060067047A1 (en) * 2004-09-30 2006-03-30 Pfahnl Andreas C Modular liquid cooling of electronic assemblies
DE102006051904A1 (de) 2006-11-03 2008-05-15 Rittal Gmbh & Co. Kg Geräteanordnung mit einem Schaltschrank und einem Kühlgerät
WO2009141610A1 (fr) 2008-05-20 2009-11-26 Semper Holdings Limited Unité de refroidissement montée dans une baie

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015215535A1 (de) * 2015-08-14 2017-02-16 SCHäFER WERKE GMBH Spritzschutz für einen Wärmetauscher in einem Schrank für elektronische Komponenten
DE102015215535B4 (de) 2015-08-14 2019-02-21 SCHäFER WERKE GMBH Kühleinrichtung mit einem Wärmetauscher und einem Spritzschutz sowie Vorrichtung mit einem Gehäuse und einer solchen Kühleinrichtung
DE102016201723A1 (de) * 2016-02-04 2017-08-10 SCHäFER WERKE GMBH Sidecooler mit einem Wärmetauscher zur Anordnung neben einem Schrank für elektronische Komponenten
DE102016201723B4 (de) 2016-02-04 2019-03-07 SCHäFER WERKE GMBH Sidecooler mit einem Wärmetauscher zur Anordnung neben einem Schrank für elektronische Komponenten
DE102016107531B3 (de) * 2016-04-22 2017-07-13 Rittal Gmbh & Co. Kg Schaltschrankanordnung mit einem in einem Schaltschrankgehäuse aufgenommenen Kühlgerät
CN109075541A (zh) * 2016-04-22 2018-12-21 里塔尔有限责任两合公司 包括容纳在电外壳壳体中的冷却装置的电外壳组件
US10765035B2 (en) 2016-04-22 2020-09-01 Rittal Gmbh & Co. Kg Electrical enclosure assembly comprising a cooling device which is received in an electrical enclosure housing

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