EP2107328B1 - Vaporiser - Google Patents
Vaporiser Download PDFInfo
- Publication number
- EP2107328B1 EP2107328B1 EP09004110A EP09004110A EP2107328B1 EP 2107328 B1 EP2107328 B1 EP 2107328B1 EP 09004110 A EP09004110 A EP 09004110A EP 09004110 A EP09004110 A EP 09004110A EP 2107328 B1 EP2107328 B1 EP 2107328B1
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- EP
- European Patent Office
- Prior art keywords
- evaporator
- flow
- fluid
- refrigerant
- fluid passages
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0085—Evaporators
Definitions
- the invention relates to an evaporator, in particular for a motor vehicle, and a device for cooling a heat source of a motor vehicle
- DE 10 2004 036 951 A1 proposes to use a built-up of parallel, interconnected plates heat exchanger, the type of which is also referred to as a stacked-plate heat exchanger to use as an evaporator of a refrigeration cycle of a motor vehicle.
- a plate type heat exchanger used as an evaporator in order to ensure sufficient evaporation and, in particular, to ensure sufficient overheating of the vaporized refrigerant, it is required that the plate length in the flow direction of the refrigerant be sufficiently large, thereby being generally larger than a plate width across to the flow direction of the refrigerant. This results in restrictions on the dimensions of the evaporator depending on the given space.
- the US 2002/0179 295 A1 discloses a cullet evaporator for an automotive air conditioning system, wherein a dimension "l" is between 20 mm and 55 mm.
- FIG. 8 shows in FIG. 8 an evaporator, in particular for a motor vehicle, comprising a plurality of plates stacked parallel to one another in a vertical direction with aligned apertures for supplying and discharging a first fluid designed as a refrigerant and a second fluid, wherein between two adjacent plates, a flow channel of the first type for guiding the first fluid in alternation with a flow channel of the second type for guiding the second fluid are formed, wherein a heat transfer surface of the plates has a length in the flow direction of the refrigerant and a perpendicular thereto Width, wherein the refrigerant the flow channels in a first, one or more of the flow channels of the first kind comprehensive flood and at least one of the first flood following a deflection subsequent, one or more of the flow channels of the first kind flowing through the second flood.
- the refrigerant flows through at least a first and second tide of the evaporator .
- a tide in the context of the invention is to be understood by the evaporator over its length sweeping flow path of the refrigerant, wherein successive floods generally parallel to each other and in the opposite direction, so that the refrigerant undergoes a deflection between the two successive floods. Due to the deflection and the passage of successive floods, the flow path of the refrigerant in the evaporator is extended even in a short design, so that sufficient overheating can be ensured.
- the ratio of the length to the width UB is not less than about 0.5, in particular not less than about 0.7.
- the heat exchanger is designed with respect to the refrigerant in such a design with exactly two floods useful as a U-flow heat exchanger.
- the refrigerant flows through at least a third, one or more flow channels of the first kind comprehensive tide, which follows a secondary flow downstream of the second deflection.
- the second tide has at least as many flow channels as the first tide and up to 50% more flow channels than the first tide.
- the third tide has at least as many flow channels as the second tide and up to 200% more flow channels than the second tide.
- “approximately equal” means that a number of flow channels of one tide deviate slightly from the number of the other two tides.
- the number of flow channels of the first and third floods can be six and the number of second floods seven.
- the second fluid flows through the evaporator in at least two floods, each comprising one or more of the flow channels of the second type.
- the evaporator would be expediently designed as a U-flow heat exchanger with respect to the second fluid.
- it can also be designed in a simple manner as an I-flow heat exchanger with only one tide for the second fluid.
- more than two floods may be provided for the second fluid.
- the second fluid is a liquid coolant.
- a separation of successive floods is formed by a special plate different from other plates, which has an obstruction instead of one or more of the openings.
- a multi-flow evaporator is designed according to the design of a plate heat exchanger in a simple manner.
- the special plate has both an obstruction for the separation of floods of Refrigerant as well as an obstruction to separate flooding of the second fluid. In this way, the number of special plates is kept very small and the number of other, generally formed as equal parts plates of the heat exchanger is kept particularly large.
- the flow direction of the last of the floods is generally preferred for the flow direction of the last of the floods to be essentially in the direction of the force of gravity. This can prevent the refrigerant from accumulating in the evaporator.
- substantially in the direction of gravity is thus also to be understood any deviation from the exact direction of gravity, which still allows a sufficiently large influence of gravity on the outflow of the refrigerant.
- An inventive evaporator is particularly well suited to be provided in a refrigerant circuit or the air conditioning system of a motor vehicle in order to cool a heat source of the motor vehicle via a coolant circuit. Due to the compact design of the evaporator, the increasingly critical space conditions in modern motor vehicles can be taken into account.
- the heat source is a traction battery of the motor vehicle, in particular a lithium-ion battery.
- a traction battery of the motor vehicle in particular a lithium-ion battery.
- Such batteries which are used not only in pure electric vehicles but especially in hybrid vehicles with an electric motor and an internal combustion engine, high demands are placed on the cooling to ensure durability and reliability.
- an inventive, small-sized evaporator of high heat exchanger performance which is arranged between a coolant circuit and a particular air conditioning of the vehicle serving refrigeration circuit (also called "chiller") is particularly suitable.
- the compressor of the refrigeration circuit may expediently be arranged directly downstream of the second evaporator. This is to be understood in particular that no collector between evaporator and compressor is arranged and space reasons, no integrated into the evaporator collector is provided.
- the schematic sectional view Fig. 1 shows a vaporizer according to the prior art.
- a plurality of plates 1 are stacked in parallel in a vertical direction h, wherein a flow channel of the first type 2 and a flow channel of the second type 3 alternately remain between two plates.
- the plates 1 have mutually aligned apertures 1 a, 1 b, are formed by the tubular, extending in the vertical direction feeds and discharges for a refrigerant or first fluid and a second fluid of the evaporator.
- the openings 1a, 1 b in a known manner alternately raised edges (not shown), which are soldered sealingly with the adjacent plate.
- the plates are made of an aluminum alloy.
- the stack of plates 1 is closed in a known manner at its two ends by end plates 9, to which the supply lines and outlets for the refrigerant and the second fluid are attached.
- Fig. 2 shows a first embodiment of an evaporator according to the invention, in which the evaporator with respect to the refrigerant in three floods 4, 5, 6 is divided.
- the separation of the flow channels 1 in the individual floods 4, 5, 6 takes place by special plates 7, in which at least one of the openings 1a, 1b is replaced by an obstruction 7a.
- the obstructions 7a prevent the refrigerant from a complete flow through the supply or discharge in the vertical direction.
- a width direction of the evaporator is perpendicular to the plane of the drawing Fig. 2 and thus perpendicular to the longitudinal direction and to the vertical direction h.
- the plates 1 have between the feeders and drains 1a, 1b a heat transferring surface having a length L in the longitudinal direction and a width B in the width direction.
- L is about 4 cm and B about 5.5 cm. This results in a ratio of UB of about 0.73.
- a height H of the stack of plates 1 is about 4 cm.
- the external dimensions of the evaporator for this particular example have a total length of 8.8 cm, a total width of 6.2 cm and a height of 4 cm.
- the plates 1 Between the individual plates 1 no turbulence inserts are provided at least on the side of the refrigerant. Depending on requirements, the plates 1 have indentations and structuring in order to increase the surface area and introduce turbulence into the flowing refrigerant.
- the flow channels of the second type 3 are shown by broken lines and are in the present case flows through by a liquid coolant of a coolant circuit as a second fluid
- the feeds and discharges for the second fluid are not shown.
- Fig. 3 shows a further embodiment of an evaporator according to the invention.
- the refrigerant only flows through two floods 4, 5, so that the throughflow path of the refrigerant as a whole is U-shaped (U-flow heat exchanger).
- the dimensions of the plates 1 are the same as in the first embodiment.
- the path of the coolant through the flow channels of the second type 3 is divided into a plurality of floods.
- Fig. 3 a representation of the floods of the second fluid or coolant, wherein the illustration Fig. 2 shows the floods of the refrigerant of the same evaporator.
- both fluids are divided into several floods, it may be expedient for one or more of the special plates 7 to have both an obstruction for the first fluid and an obstruction for the second fluid. This makes it possible to reduce the number of special plates required and increase the total number of identical parts of the evaporator.
- Fig. 4 shows a device for cooling a heat source 10 of a motor vehicle, in this case a lithium-ion battery of a hybrid drive.
- the battery 10 is cooled by a circuit with liquid coolant, which is circulated via a circulation pump 11.
- the heat absorbed by the battery 10 is dissipated via a heat exchanger 12, the an inventive evaporator according to one of the preceding embodiments is.
- the evaporator 12 is integrated in a refrigeration circuit 13, which also serves for air conditioning of the motor vehicle.
- the refrigerant is compressed by a compressor 14 and subsequently cooled by a condenser or gas cooler 15
- the condenser or gas cooler 15 below are an air conditioner 16 and the evaporator 12 according to the invention connected in parallel, wherein before each of the evaporator 12, 16 each have an expansion element 16a, 12a is arranged.
- a fan 17 delivers air for conditioning by the A / C evaporator 16.
- Fig. 5 shows a modification of the device Fig. 4 in which the coolant circuit in addition to the evaporator 16 still has a parallel-connected auxiliary cooler 18, which is flowed around by outside air.
- the coolant can selectively flow through the evaporator 12, the Bruchler 18 or both heat exchangers 12, 18 to ensure optimal cooling of battery 10 and the vehicle interior in all operating situations.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air-Conditioning For Vehicles (AREA)
Description
Die Erfindung betrifft einen Verdampfer, insbesondere für ein Kraftfahrzeug, und eine Vorrichtung zur Kühlung einer Wärmequelle eines KraftfahrzeugsThe invention relates to an evaporator, in particular for a motor vehicle, and a device for cooling a heat source of a motor vehicle
Die
Dieses Dokument, welches als nächster Stand der Technik betrachtet werden kann, zeigt in Figur 8 einen Verdampfer, insbesondere für ein Kraftfahrzeug, umfassend eine Mehrzahl von parallel zueinander in einer Hochrichtung gestapelten Platten mit fluchtend angeordneten Durchbrechungen zur Zuführung und Abführung eines als Kältemittel ausgebildeten ersten Fluids und eines zweiten Fluids, wobei zwischen zwei benachbarten Platten ein Strömungskanal erster Art zur Führung des ersten Fluids im Wechsel mit einem Strömungskanal zweiter Art zur Führung des zweiten Fluids ausgebildet sind, wobei eine wärmeübertragende Fläche der Platten eine Länge in Strömungsrichtung des Kältemittels und eine hierzu senkrechte Breite aufweist, wobei das Kältemittel die Strömungskanäle in einer ersten, einen oder mehrere der Strömungskanäle erster Art umfassenden Flut und zumindest einer der ersten Flut nach einer Umlenkung nachfolgenden, einen oder mehrere der Strömungskanäle erster Art umfassenden zweiten Flut durchströmt.This document, which can be regarded as the closest prior art, shows in FIG. 8 an evaporator, in particular for a motor vehicle, comprising a plurality of plates stacked parallel to one another in a vertical direction with aligned apertures for supplying and discharging a first fluid designed as a refrigerant and a second fluid, wherein between two adjacent plates, a flow channel of the first type for guiding the first fluid in alternation with a flow channel of the second type for guiding the second fluid are formed, wherein a heat transfer surface of the plates has a length in the flow direction of the refrigerant and a perpendicular thereto Width, wherein the refrigerant the flow channels in a first, one or more of the flow channels of the first kind comprehensive flood and at least one of the first flood following a deflection subsequent, one or more of the flow channels of the first kind flowing through the second flood.
Es ist die Aufgabe der Erfindung, einen Verdampfer anzugeben, der bei hoher Tauscherleistung und sichergestellter Überhitzung des Kältemittels eine besonders kompakte Form und Abmessung aufweist.It is the object of the invention to provide an evaporator which has a particularly compact shape and dimension with high heat exchanger performance and ensured overheating of the refrigerant.
Diese Aufgabe wird für einen eingangs genannten Verdampfer erfindungsgemäß mit den Merkmalen des Anspruchs 1 gelöst. Durch die Beschränkung des Verhältnisses von Länge zu Breite der wärmeübertragenden Fläche auf einen Wert von weniger oder gleich 1,3 kann ein in Strömungsrichtung des Kältemittels besonders kurzbauender Verdampfer in Plattenbauweise verwirklicht werden. Um bei einer solchen kurzen Bauweise eine ausreichende Überhitzung des Kältemittels am Verdampferaustritt in allen Betriebssituationen sicherzustellen und somit eine Beschädigung eines Verdichters des Kältekreises durch angesaugtes flüssiges Kältemittel wirksam zu verhindern ist es zudem erfindungsgemäß vorgesehen, dass das Kältemittel zumindest eine erste und zweite Flut des Verdampfers durchströmt. Unter einer Flut im Sinne der Erfindung ist dabei ein den Verdampfer über seine Länge durchgreifender Strömungsweg des Kältemittels zu verstehen, wobei aufeinanderfolgende Fluten im Allgemeinen parallel zueinander und in Gegenrichtung verlaufen, so dass das Kältemittel zwischen den beiden aufeinanderfolgenden Fluten eine Umlenkung erfährt. Durch die Umlenkung und das Durchströmen aufeinanderfolgender Fluten wird der Strömungsweg des Kältemittels in dem Verdampfer auch bei kurzer Bauform verlängert, so dass eine ausreichende Überhitzung sichergestellt werden kann.This object is achieved according to the invention for an evaporator mentioned above with the features of
Besonders bevorzugt ist das Verhältnis der Länge zu der Breite UB nicht kleiner als etwa 0,5, insbesondere nicht kleiner als etwa 0,7. Durch eine solche Wahl der Verhältnisse von Länge und Breite kann der erfindungsgemäße Verdampfer in jeder Raumrichtung relativ kurzbauend ausgelegt werden, so dass insbesondere durch grobe Annäherung an eine quadratische Umrissform der einzelnen Tauscherplatten eine besonders kompakte Bauform ermöglicht ist.Particularly preferably, the ratio of the length to the width UB is not less than about 0.5, in particular not less than about 0.7. By such a choice of ratios of length and width, the evaporator according to the invention can be designed relatively short construction in each spatial direction, so that a particularly compact design is made possible in particular by rough approximation to a square outline of the individual exchanger plates.
In einer bevorzugten Ausführungsform der Erfindung gilt für das Verhältnis der Anzahl der Strömungskanäle der zweiten Flut n2 zu der Anzahl der Strömungskanäle der ersten Flut die Beziehung 1 <= n2/n1 <= 3. Dies bedeutet, dass die Anzahl der Strömungskanäle der zweiten Flut wenigstens so groß ist wie die Anzahl der Strömungskanäle der ersten Flut und bis zu 200% größer. Durch die Zunahme der Anzahl der Strömungskanäle beim Wechsel von der ersten Flut auf die zweite Flut wird eine ausreichende Überhitzung des verdampfenden Kältemittels auf besonders sichere Weise gewährleistet.In a preferred embodiment of the invention, the relationship between the number of flow channels of the second flow n2 and the number of flow channels of the first flow is 1 <= n2 / n1 <= 3. This means that the number of flow channels of the second flow is at least as large as the number of flow channels of the first tide and up to 200% larger. By increasing the number of flow channels in the Changing from the first flood to the second flood ensures sufficient overheating of the evaporating refrigerant in a particularly secure manner.
Je nach Anforderungen kann bei einer solchen Ausführungsform vorgesehen sein, dass genau zwei Fluten für das Kältemittel vorgesehen sind. Der Wärmetauscher ist bezüglich des Kältemittels bei einer solchen Ausführung mit genau zwei Fluten zweckmäßig als U-flow-Wärmetauscher ausgebildet.Depending on the requirements may be provided in such an embodiment that exactly two floods are provided for the refrigerant. The heat exchanger is designed with respect to the refrigerant in such a design with exactly two floods useful as a U-flow heat exchanger.
Bei einer besonders bevorzugten Ausführungsform der Erfindung ist es vorgesehen, dass das Kältemittel zumindest eine dritte, einen oder mehrere Strömungskanäle erster Art umfassende Flut durchströmt, die auf eine der zweiten Flut nachgeordnete zweite Umlenkung folgt. Besonders bevorzugt gilt dabei für das Verhältnis der Anzahl der Strömungskanäle der zweiten Flut n2 zu der Anzahl der Strömungskanäle der ersten Flut n1 die Beziehung 1 <= n2/n1 <= 1,5. Alternativ oder ergänzend gilt für eine solche Ausführungsform mit drei Fluten für das Verhältnis der Anzahl der Strömungskanäle der dritten Flut n3 zu der Anzahl der Strömungskanäle der zweiten Flut n2 die Beziehung 1 <= n3/n2 <= 3, wobei besonders bevorzugt beide der vorgenannten Beziehungen gelten. Somit hat die zweite Flut wenigsten so viele Strömungskanäle wie die erste Flut und bis zu 50% mehr Strömungskanäle als die erste Flut. Die dritte Flut hat wenigstens so viele Strömungskanäle wie die zweite Flut und bis zu 200% mehr Strömungskanäle als die zweite Flut. Insgesamt wird hierdurch der Strömungsweg des Kältemittels durch den Verdampfer weiter vergrößert, wobei durch die Zunahme der Anzahl der Strömungskanäle eine besonders sichere Überhitzung des Kältemittels am Austritt des Verdampfers erreicht. Grundsätzlich ist im Sinne der Erfindung nicht ausgeschlossen, noch eine vierte und weitere Fluten des Verdampfers vorzusehen.In a particularly preferred embodiment of the invention, it is provided that the refrigerant flows through at least a third, one or more flow channels of the first kind comprehensive tide, which follows a secondary flow downstream of the second deflection. For the ratio of the number of flow channels of the second flow n2 to the number of flow passages of the first flow n1, the
Alternativ und im Sinne einer einfachen Montage des Verdampfers kann die Anzahl der Strömungskanäle der ersten Flut (n1) und die Anzahl der Strömungskanäle der zweiten Flut (n2) und die Anzahl der Strömungskanäle der dritten Flut (n3) annähernd gleich oder identisch sein (n1=n2=n3).Alternatively and in the sense of a simple assembly of the evaporator, the number of flow channels of the first flow (n1) and the number of flow channels of the second flow (n2) and the number of flow channels of the third flow (n3) can be approximately equal or identical (n1 = n2 = n3).
Durch eine identische Anzahl der Strömungskanäle der drei Fluten ist auch die Plattenanzahl der Teilstapel zur Bildung der drei Fluten identisch. Somit ist eine Unterscheidung der Teitstapel nach späterer Einbaulage überflüssig. Der logistische Aufwand in der Produktion wird durch eine derartige Ausgestaltung des Verdampfers erheblich vereinfacht.By an identical number of flow channels of the three floods and the number of plates of the sub-stacks to form the three floods is identical. Thus, a distinction of Teitstapel after later installation position is unnecessary. The logistical effort in production is greatly simplified by such a design of the evaporator.
"Annähernd gleich" im Sinne der Erfindung bedeutet, dass eine Anzahl von Strömungskanälen einer Flut geringfügig von der Anzahl der beiden anderen Fluten abweicht. Beispielsweise kann die Anzahl der Strömungskanäle der ersten und dritten Flut sechs betragen und die Anzahl der zweiten Flut sieben.For the purposes of the invention, "approximately equal" means that a number of flow channels of one tide deviate slightly from the number of the other two tides. For example, the number of flow channels of the first and third floods can be six and the number of second floods seven.
Allgemein vorteilhaft ist es zur Verbesserung des Wärmeübergangs zwischen den beiden Fluiden vorgesehen, dass das zweite Fluid den Verdampfer in zumindest zwei Fluten durchströmt, die jeweils einen oder mehrere der Strömungskanäle zweiter Art umfassen. Bei einer Ausführung mit genau zwei Fluten bezüglich des zweiten Fluids wäre der Verdampfer zweckmäßig als U-flow-Wärmetauscher bezüglich des zweiten Fluids auszubilden. Alternativ kann er aber auch auf einfache Weise als I-flow-Wärmetauscher mit nur einer Flut für das zweite Fluid ausgebildet sein. Je nach Anforderungen können auch mehr als zwei Fluten für das zweite Fluid vorgesehen sein. Bei dem zweiten Fluid handelt es sich um ein flüssiges Kühlmittel.Generally, it is provided to improve the heat transfer between the two fluids that the second fluid flows through the evaporator in at least two floods, each comprising one or more of the flow channels of the second type. In an embodiment with exactly two floods with respect to the second fluid, the evaporator would be expediently designed as a U-flow heat exchanger with respect to the second fluid. Alternatively, however, it can also be designed in a simple manner as an I-flow heat exchanger with only one tide for the second fluid. Depending on requirements, more than two floods may be provided for the second fluid. The second fluid is a liquid coolant.
Bei einer kostensparenden und einfachen Bauform der Erfindung ist es vorgesehen, dass eine Trennung aufeinanderfolgender Fluten durch eine von anderen Platten verschiedene Sonderplatte ausgebildet ist, die anstelle einer oder mehrerer der Durchbrechungen eine Versperrung aufweist. Durch entsprechende Anordnung von Sonderplatten mit solchen Versperrungen ist auf einfache Weise ein mehrflutiger Verdampfer nach der Bauart eines PlattenWärmetauschers ausgebildet. In besonders zweckmäßiger Detailgestaltung hat die Sonderplatte sowohl eine Versperrung zur Trennung von Fluten des Kältemittels als auch eine Versperrung zur Trennung von Fluten des zweiten Fluids. Auf diese Weise wird die Anzahl der Sonderplatten besonders klein gehalten und die Anzahl der anderen, im Allgemeinen als Gleichteile ausgebildeten Platten des Wärmetauschers wird besonders groß gehalten.In a cost-saving and simple design of the invention, it is provided that a separation of successive floods is formed by a special plate different from other plates, which has an obstruction instead of one or more of the openings. By appropriate arrangement of special plates with such obstructions a multi-flow evaporator is designed according to the design of a plate heat exchanger in a simple manner. In a particularly expedient detail design, the special plate has both an obstruction for the separation of floods of Refrigerant as well as an obstruction to separate flooding of the second fluid. In this way, the number of special plates is kept very small and the number of other, generally formed as equal parts plates of the heat exchanger is kept particularly large.
Allgemein vorteilhaft sind zwischen den Platten eines erfindungsgemäßen Verdampfers keine Turbulenzeinlagen vorgesehen. Durch Turbulenzeinlagen wird neben erhöhten Kosten und einer aufwendigen Herstellung die Gefahr einer Verunreinigung des Kältemittels durch Flitter und andere Herstellungsrückstände der Turbulenzeinlagen eingebracht, die insbesondere bei der Anbindung an einen Kältekreis mit einem Verdichter und einem Expansionsorgan die Gefahr von Beschädigungen birgt. Zur Vergrößerung der wärmeübertragenden Eigenschaften können anstelle von separaten Turbulenzeinlagen Einprägungen in den Platten vorgesehen sein, durch deren Struktur sowohl eine Vergrößerung der Oberfläche als auch die Einbringung von Turbulenzen in die strömenden Fluide erzielt wird.In general, no turbulence inserts are provided between the plates of an evaporator according to the invention. By turbulence inserts in addition to increased costs and costly production, the risk of contamination of the refrigerant by tinsel and other manufacturing residues of turbulence inserts is introduced, which carries the risk of damage especially when connected to a refrigerant circuit with a compressor and an expansion device. To increase the heat-transmitting properties, instead of separate turbulence inserts, embossments may be provided in the plates, the structure of which achieves both an increase in the surface area and the introduction of turbulence into the flowing fluids.
Bezüglich einer räumlichen Orientierung des Verdampfers ist es allgemein bevorzugt vorgesehen, dass die Strömungsrichtung der letzten der Fluten im Wesentlichen in Richtung der Schwerkraft verläuft. Hierdurch kann verhindert werden, dass sich Kältemittel in dem Verdampfer ansammelt. Unter "im Wesentlichen in Richtung der Schwerkraft" ist somit auch jede Abweichung von der genauen Schwerkraftsrichtung zu verstehen, die noch einen ausreichend großen Einfluss der Schwerkraft auf die Ausströmung des Kältemittels zulässt.With regard to a spatial orientation of the evaporator, it is generally preferred for the flow direction of the last of the floods to be essentially in the direction of the force of gravity. This can prevent the refrigerant from accumulating in the evaporator. By "substantially in the direction of gravity" is thus also to be understood any deviation from the exact direction of gravity, which still allows a sufficiently large influence of gravity on the outflow of the refrigerant.
Die Aufgabe der Erfindung wird auch durch eine Vorrichtung nach dem Anspruchs 12 gelöst. Ein erfindungsgemäßer Verdampfer ist besonders gut geeignet, in einem Kältemittelkreislauf bzw. der Klimaanlage eines Kraftfahrzeugs vorgesehen zu werden, um über einen Kühlmittelkreislauf eine Wärmequelle des Kraftfahrzeugs zu kühlen. Durch die kleinbauende Form des Verdampfers kann den immer kritisch werdenden Bauraumbedingungen bei modernen Kraftfahrzeug Rechnung getragen werden.The object of the invention is also achieved by a device according to
Bei einer bevorzugten Detailgestaltung der Vorrichtung handelt es sich bei der Wärmequelle um eine Fahrbatterie des Kraftfahrzeugs, insbesondere um eine Lithium-lonen-Batterie. An solche Batterien, die nicht nur bei reinen Elektrofahrzeugen sondern insbesondere auch bei Hybridfahrzeugen mit einem Elektro- und einem Verbrennungsmotor Einsatz finden, werden hohe Anforderungen an die Kühlung gestellt, um Lebensdauer und Betriebssicherheit zu gewährleisten. Hierzu ist ein erfindungsgemäßer, kleinbauender Verdampfer von hoher Tauscherleistung, der zwischen einem Kühlmittelkreislauf und einem insbesondere der Klimatisierung des Fahrzeugs dienenden Kältekreislauf angeordnet ist (auch "Chiller" genannt) besonders geeignet.In a preferred detailed design of the device, the heat source is a traction battery of the motor vehicle, in particular a lithium-ion battery. Such batteries, which are used not only in pure electric vehicles but especially in hybrid vehicles with an electric motor and an internal combustion engine, high demands are placed on the cooling to ensure durability and reliability. For this purpose, an inventive, small-sized evaporator of high heat exchanger performance, which is arranged between a coolant circuit and a particular air conditioning of the vehicle serving refrigeration circuit (also called "chiller") is particularly suitable.
Da der erfindungsgemäße Verdampfer eine Überhitzung des Kältemittels in seinem Austrittsbereich auf besonders sichere Weise gewährleistet, kann zweckmäßig der Verdichter des Kältekreislaufs dem zweiten Verdampfer unmittelbar nachgeordnet sein. Hierunter ist insbesondere zu verstehen, dass kein Sammler zwischen Verdampfer und Verdichter angeordnet ist und aus Bauraumgründen auch kein in den Verdampfer integrierter Sammler vorgesehen ist.Since the evaporator according to the invention ensures overheating of the refrigerant in its outlet region in a particularly secure manner, the compressor of the refrigeration circuit may expediently be arranged directly downstream of the second evaporator. This is to be understood in particular that no collector between evaporator and compressor is arranged and space reasons, no integrated into the evaporator collector is provided.
Weitere Vorteile und Merkmale der Erfindung ergeben sich aus den nachfolgend beschriebenen Ausführungsbeispielen sowie aus den abhängigen Ansprüchen.Further advantages and features of the invention will become apparent from the embodiments described below and from the dependent claims.
Nachfolgend werden mehrere bevorzugte Ausführungsbeispiele der Erfindung beschrieben und anhand der anliegenden Zeichnungen näher erläutert.
- Fig. 1
- zeigt eine schematische Darstellung des Verdampfers nach dem Stand der Technik.
- Fig. 2
- zeigt eine schematische Schnittansicht eines ersten Ausfüh- rungsbeispiels eines erfindungsgemäßen Verdampfers.
- Fig. 3
- zeigt eine schematische Schnittansicht eines zweiten Ausfüh- rungsbeispiels eines erfindungsgemäßen Verdampfers.
- Fig. 4
- zeigt ein erstes Beispiel einer Vorrichtung zur Kühlung einer Wärmequelle mit einem erfindungsgemäßen Verdampfer.
- Fig. 5
- zeigt eine Abwandlung der Vorrichtung aus
Fig. 4 .
- Fig. 1
- shows a schematic representation of the evaporator according to the prior art.
- Fig. 2
- shows a schematic sectional view of a first exemplary embodiment of an evaporator according to the invention.
- Fig. 3
- shows a schematic sectional view of a second exemplary embodiment of an evaporator according to the invention.
- Fig. 4
- shows a first example of a device for cooling a heat source with an evaporator according to the invention.
- Fig. 5
- shows a modification of the device
Fig. 4 ,
Die schematische Schnittdarstellung
Der Stapel von Platten 1 ist auf bekannte Weise an seinen beiden Enden durch Abschlussplatten 9 abgeschlossen, an denen auch die Zuleitungen und Ableitungen für das Kältemittel und das zweite Fluid angebracht sind.The stack of
Die Durchströmung des Verdampfers nach dem Stand der Technik mit Kältemittel erfolgt wie durch die Pfeile angedeutet in nur einer Flut nach Art eines I-flow-Wärmetauschers von der Zuführung 1 a zu der Abführung 1 b.The flow through the evaporator according to the prior art with refrigerant takes place as indicated by the arrows in only one tide in the manner of an I-flow heat exchanger from the
Eine Breitenrichtung des Verdampfers verläuft senkrecht zur Zeichnungsebene der
Die erste Flut 4 umfasst vorliegend eine Anzahl n1 von zwei Strömungskanälen erster Art 2, die zweite Flut 5 umfasst eine Anzahl n2 von drei Strömungskanälen 2 und die dritte Flut umfasst eine Anzahl n3 von vier Strömungskanälen 2. Somit gelten für die Verhältnisse der Anzahlen von Strömungskanälen die Bedingungen:
- 1 <= n2/n1 = 1,5 <= 1,5 und
- 1 <= n3/n2 = 1,33 <= 3.
- 1 <= n2 / n1 = 1.5 <= 1.5 and
- 1 <= n3 / n2 = 1.33 <= 3.
Durch die Zunahme der jeweiligen Anzahl der Strömungskanäle 2 in aufeinander folgenden Fluten 4, 5, 6 wird die Expansion des Kältemittels berücksichtigt und insbesondere eine ausreichende Überhitzung des Kältemittels am Austritt des Verdampfers sichergestellt.Due to the increase in the respective number of
Zwischen den einzelnen Platten 1 sind zumindest auf der Seite des Kältemittels keine Turbulenzeinlagen vorgesehen. Die Platten 1 haben je nach Anforderungen Einprägungen und Strukturierungen, um die Oberfläche zu vergrößern und Turbulenzen in das strömende Kältemittel einzubringen.Between the
Die in Strömungskanäle zweiter Art 3 sind durch unterbrochene Linien dargestellt und werden vorliegend von einem flüssigen Kühlmittel eines Kühlmittelkreislaufs als zweites Fluid durchströmt Die Zuführungen und Abführungen für das zweite Fluid sind nicht dargestellt.The flow channels of the
Die Anzahl der Strömungskanäle der ersten Flut 4 ist in diesem Beispiel n1=3 und die Anzahl der Strömungskanäle der zweiten Flut 5 ist n2=4. Die Anzahl der Strömungskanäle erfüllt somit die Bedingung
1 <= n2/n1 1 = 1,33 <= 3.The number of flow channels of the
1 <= n2 /
Bei einer weiteren Ausführungsform der Erfindung ist auch der Weg des Kühlmittels durch die Strömungskanäle zweiter Art 3 in mehrere Fluten unterteilt. Insbesondere zeigt dabei die
Der Verdampfer 12 ist in einem Kältekreislauf 13 integriert, der zugleich zur Klimatisierung des Kraftfahrzeugs dient. Hierzu wird das Kältemittel über einen Verdichter 14 verdichtet und nachfolgend über einen Kondensator oder Gaskühler 15 gekühlt Dem Kondensator oder Gaskühler 15 nachfolgend sind ein Klimaverdampfer 16 und der erfindungsgemäße Verdampfer 12 parallel geschaltet, wobei vor jedem der Verdampfer 12, 16 jeweils ein Expansionsorgan 16a, 12a angeordnet ist. Eine Lüfter 17 fördert Luft zur Konditionierung durch den Klimaverdampfer 16.The
Es sind andere Verschaltungen der Verdampfer 12, 16 wie etwa seriell, insbesondere mit schaltbaren Bypässen, denkbar. Ebenso kann für beide Verdampfer 12, 16 ein gemeinsames Expansionsorgan vorgesehen sein.There are other interconnections of the
Claims (14)
- An evaporator, particularly for a motor vehicle, comprising a plurality of plates (1) stacked parallel with one another in a vertical direction, with through opening (1a, 1b) arranged aligned for the purpose of supplying and draining off a first fluid embodied as refrigerant and a second fluid embodied as liquid coolant, wherein between two adjoining plates (1) a fluid passage (2) of the first type for conducing the first fluid is formed alternatingly with a fluid passage (3) of the second type for conducing the second fluid,
wherein a heat transferring surface of the plates (1) has a length (L) in the direction of flow of the refrigerant and a width (B) perpendicular thereto, wherein the evaporator can be integrated both info a refrigerant circuit and info a coolant circuit,
wherein the ratio of length to width (L/B) is no greater than approximately 1.3,
wherein the refrigerant flows through the fluid passages (2) in a first flow (4) comprising one or more of the fluid passages (2) of the first type, and through at least one second flow (5) that follows the first flow downstream of a reversal (8) and comprises one or more of the fluid passages (2) of the first type. - The evaporator according to claim 1, characterized in that the ratio of length to width L/B is no less than approximately 0.5, particularly no less than approximately 0.7.
- The evaporator according to any one of the preceding claims, characterized in that for the ratio of the number of fluid passages of the second flow (n2) to the number of fluid passages of the first flow (n1), the relationship 1 <= n2/n1 <= 3 is true.
- The evaporator according to claim 3, characterized in that precisely two flows (4, 5) for the refrigerant are provided.
- The evaporator according to any one of claims 1 to 3, characterized in that the refrigerant flows through a third flow (6), which comprises one or more fluid passages (2) of the first type and follows a second reversal (8), which is downstream of the second flow (5).
- The evaporator according to claim 5, characterized in that for the ratio of the number of fluid passages of the second flow (n2) to the number of fluid passages of the first flow (n1), the relationship 1 <= n2/n1 <= 1.5 is true.
- The evaporator according to claim 5 or 6, characterized in that for the ratio of the number of fluid passages of the third flow (n3) to the number of fluid passages of the second flow (n2), the relationship 1 <= n3/n2 <= 3 is true.
- The evaporator according to any one of claims 5 to 7, characterized in that the number of fluid passages of the third flow (n3) and the number of fluid passages of the second flow (n2) and the number of fluid passages of the first flow (n1) are approximately equal or identical.
- The evaporator according to any one of the preceding claims, characterized in that the second fluid flows through the evaporator in at least two flows, each of which comprises one or more of the fluid passages (3) of the second type.
- The evaporator according to any one of the preceding claims, characterized in that a separation of successive flows (4, 5, 6) is formed by a special plate (7) which is different from the other plates (1), having a barrier (7a) in place of one or more of the through openings.
- The evaporator according to claim 10, characterized in that the special plate (7) has both a barrier (7a) for separating flows of the refrigerant and a barrier for separating flows of the second fluid.
- A device for cooling a heat source of a motor vesicle, comprising a refrigerant circuit with a compressor (14), a condenser or gas cooler (15), a first evaporator (16) for air conditioning the passenger space of a vehicle and a second evaporator (12), wherein the second evaporator (12) is in thermal communication with a coolant circuit that cools the heat source (10), wherein the second evaporator (12) is embodied as an evaporator according to any one of claims 1 to 11.
- The device according to claim 12, characterized in that the heat source (10) is a main battery for the motor vehicle, more particularly, a lithium-ion battery.
- The device according to claim 12 or 13, characterized in that in the refrigerant circuit, the compressor (14) is arranged immediately downstream of the second evaporator (12).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008017113A DE102008017113A1 (en) | 2008-04-02 | 2008-04-02 | Evaporator for use in cooling device of heat source of motor vehicle, has plates whose length to width ratio is not greater than specific value, and refrigerant flows through flow passages in bank after reversal of direction of refrigerant |
DE102008044673 | 2008-08-28 |
Publications (2)
Publication Number | Publication Date |
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EP2107328A1 EP2107328A1 (en) | 2009-10-07 |
EP2107328B1 true EP2107328B1 (en) | 2012-07-11 |
Family
ID=40846998
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP09004110A Not-in-force EP2107328B1 (en) | 2008-04-02 | 2009-03-23 | Vaporiser |
Country Status (2)
Country | Link |
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US (1) | US20090249810A1 (en) |
EP (1) | EP2107328B1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011008653A1 (en) | 2011-01-14 | 2012-07-19 | Behr Gmbh & Co. Kg | Heat exchanger |
DE102011081886A1 (en) | 2011-08-31 | 2013-02-28 | Behr Gmbh & Co. Kg | Heat exchanger |
DE102012104520A1 (en) * | 2012-05-25 | 2013-11-28 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Electrical-driven vehicle has cooling circuit heat exchanger that is provided to transfer heat from first refrigerant to second refrigerant and is connected to second coolant by connection unit |
DE102015205933A1 (en) * | 2015-04-01 | 2016-10-06 | Mahle International Gmbh | Heat exchanger or chiller |
WO2017201252A1 (en) * | 2016-05-20 | 2017-11-23 | Modine Manufacturing Company | Heat exchanger and heat exchange system |
CN110186300A (en) * | 2019-06-27 | 2019-08-30 | 浙江银轮机械股份有限公司 | Plate, plate component and heat exchanger |
Family Cites Families (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2717045A (en) * | 1949-09-28 | 1955-09-06 | Daimler Benz Ag | Heating and cooling system for vehicle passenger and battery compartments |
US4016929A (en) * | 1974-06-08 | 1977-04-12 | Pfluger Apparatebau Gmbh & Co. Kg | Heat-exchanger |
US3978687A (en) * | 1975-06-23 | 1976-09-07 | Faaca Inc. | Modified evaporator for automobile air conditioning systems |
US4201263A (en) * | 1978-09-19 | 1980-05-06 | Anderson James H | Refrigerant evaporator |
JPS60173879U (en) * | 1984-04-25 | 1985-11-18 | 日産自動車株式会社 | Automotive cold storage |
US5682944A (en) * | 1992-11-25 | 1997-11-04 | Nippondenso Co., Ltd. | Refrigerant condenser |
DE4426692C1 (en) * | 1994-07-28 | 1995-09-14 | Daimler Benz Ag | Vaporiser for transporting load of reactant mass flow |
JPH116693A (en) * | 1997-04-23 | 1999-01-12 | Denso Corp | Heat-exchanger for air-conditioner in vehicle |
GB2346680A (en) * | 1999-02-11 | 2000-08-16 | Llanelli Radiators Ltd | Condenser |
JP4281175B2 (en) * | 1999-09-29 | 2009-06-17 | 株式会社デンソー | Double heat exchanger |
FR2803376B1 (en) * | 1999-12-29 | 2002-09-06 | Valeo Climatisation | EVAPORATOR WITH STACKED FLAT TUBES HAVING TWO OPPOSITE FLUID BOXES |
WO2002055947A1 (en) * | 2001-01-16 | 2002-07-18 | Zexel Valeo Climate Control Corporation | Heat exchanger |
DE10158385A1 (en) * | 2001-11-28 | 2003-06-12 | Bosch Gmbh Robert | air conditioning |
EP1530701B1 (en) * | 2002-07-05 | 2016-04-13 | MAHLE Behr GmbH & Co. KG | Heat exchanger in particular an evaporator for a vehicle air-conditioning unit |
DE10302412A1 (en) * | 2003-01-21 | 2004-07-29 | Behr Gmbh & Co. Kg | Heat exchanger, especially gas cooler for coolant circuit for vehicle air conditioning system, has manifold bent from a prefabricated strip with edges with tongues, central region with cut-outs |
FR2851503B1 (en) * | 2003-02-20 | 2008-02-15 | VENTILATION, HEATING AND / OR AIR CONDITIONING APPARATUS FOR A MOTOR VEHICLE WITH SIMULTANEOUS AIR COOLING AND A HEAT PUMP FLUID | |
JP2005030700A (en) * | 2003-07-07 | 2005-02-03 | Calsonic Kansei Corp | Tube fixing part structure of heat exchanger |
WO2005012820A1 (en) | 2003-08-01 | 2005-02-10 | Behr Gmbh & Co. Kg | Heat exchanger and method for the production thereof |
KR100518856B1 (en) * | 2003-09-04 | 2005-09-30 | 엘지전자 주식회사 | Heat exchanger of flat tube |
EP1700077A1 (en) * | 2003-12-11 | 2006-09-13 | Behr GmbH & Co. | Structural arrangement for heat-exchanging devices |
US7080683B2 (en) * | 2004-06-14 | 2006-07-25 | Delphi Technologies, Inc. | Flat tube evaporator with enhanced refrigerant flow passages |
US20060130513A1 (en) * | 2004-12-22 | 2006-06-22 | Samsung Electronics Co., Ltd. | Refrigerator |
JP2008527306A (en) * | 2005-01-14 | 2008-07-24 | ベール ゲーエムベーハー ウント コー カーゲー | Especially for automotive air conditioners |
JP4761790B2 (en) * | 2005-02-28 | 2011-08-31 | カルソニックカンセイ株式会社 | Evaporator |
JP2007163042A (en) * | 2005-12-14 | 2007-06-28 | Showa Denko Kk | Heat exchanger |
-
2009
- 2009-03-23 EP EP09004110A patent/EP2107328B1/en not_active Not-in-force
- 2009-04-02 US US12/417,491 patent/US20090249810A1/en not_active Abandoned
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US20090249810A1 (en) | 2009-10-08 |
EP2107328A1 (en) | 2009-10-07 |
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