DE202019102230U1 - Heat exchanger arrangement with at least one multi-pass heat exchanger - Google Patents

Abstract

Heat exchanger arrangement with at least one multi-pass heat exchanger, which has an outer inflow area (F) which can be flowed by a gas flow, as well as a first distributor (1), a second distributor (2) and at least one diverter distributor (4), and a plurality of pipelines (5). comprises, which of a fluid, in particular water, can be flowed through, wherein the first distributor (1) and the second distributor (2) at one end (A) of the heat exchanger assembly are arranged and the Umlenkverteiler (4) at the opposite end (B) and the pipelines (5) extend from one end (A) to the opposite end (B) and at least part of the pipelines (5) communicate with the diverter manifold (4) at a pipe end (5 ') in that at least a part of the pipelines (5) which are in communication with the deflecting distributor (4) are arranged at their pipe end (5 ') facing the deflecting distributor (4) in one Kröpfbereich (6) to the deflection manifold (4) is cranked out.

Description

The invention relates to a heat exchanger arrangement with at least one multi-pass heat exchanger, which comprises a first and a second distributor, each having a connection piece for connection to a fluid line, and at least one first deflection distributor and a plurality of tubes, the tubes being a fluid, in particular water, can be flowed through.

Such heat exchanger arrangements with at least one multi-pass heat exchanger can be used, for example, as a recooler in cooling systems for cooling a fluid used as heat transfer medium in the cooling system. The recooler is usually placed outside of a device to be cooled, for example, outside a building. If water is used as the heat transfer medium, there is therefore the risk that the heat transfer medium freezes at frost at the installation of the recooler.

Therefore, cooling systems with heat exchanger arrangements are known from the prior art, which allow emptying of the recooler in an antifreeze operation. For example, from the WO2018 / 184908 A1 a cooling system with recirculating water as the heat transfer medium is known, which contains a recooler and a water tank, wherein the recooler at a first end portion of an input collector and an output collector and at its second end portion opposite the first end portion a Umlenksammler having a first and a second branch, which are arranged V-shaped to each other, comprises. The first branch and the second branch of the Umlenksammlers are connected to each other via a arranged at its upper end connecting branch, wherein in the connecting branch a ventilation opening is arranged. Between the input collector and the first branch of the Umlenksammlers extends a rising in a flow direction first pipe assembly and between the second branch of the Umlenksammlers and the output collector extends a sloping in the flow direction second pipe assembly. The depressurized water tank communicates with an input at the input header and with an output at the output header, so that the stored in the water tank cooling water can be passed in a closed circuit through the recooler. For aerating and venting the water tank is connected via a ventilation / venting line, which opens into the ventilation opening at the connecting branch of Umlenksammlers, with the recooler in combination. The thus formed recooler thus has two in-line fitting registers with a first outgoing pipe arrangement connecting the input header to the reversing accumulator and forming a first fitting register and a second pipe arrangement forming a second fitting register between the deflector and the output collector to connect the Umlenkksammler with the output collector. In a recooling operation, the water passed through the piping assemblies is cooled by heat exchange with aspirated ambient air. For this purpose, the stocked in the water tank cooling water is passed through the recooler by means of a circulation pump. For emptying the recooler at risk of frost is provided in this known cooling system to turn off the circulation pump. When the circulation pump is switched off, the recooler automatically empties as a result of the constant ventilation of the deflection collector in conjunction with the gradient of the two pipe arrangements of the two fitting registers.

However, heat exchanger assemblies having one or more series pass filters (one-pass heat exchangers) have lower cooling efficiency compared to multi-pass systems in which the cooling medium passes through the heat exchanger (s) multiple times. To improve the cooling efficiency and to hear the cooling performance heat exchanger assemblies are therefore often used with multi-pass registers. This is especially necessary if cooling capacities between 100 and 1500 kW are to be achieved.

A cooling arrangement with a two-pass register is for example from WO 90/15299 -A known. The cooling water used as heat transfer medium flows through a heat exchanger of the cooling system twice (2-pass heat exchanger). For this purpose, a heat exchanger with a arranged at one end of the heat exchanger input collector and an outlet header and arranged at the opposite end Umlenksammler is provided, extending between the input collector and the Umlenksammler formed as Hinleitungen piping and formed between the Umlenksammler and the output collector as return lines piping extend. In a recooling operation, the cooling water is first passed through the return lines in a first pass (first pass) and through the return lines in a second pass (second pass). During the passage of the cooling water through the pipes of the two-pass heat exchanger takes place for cooling the cooling water heat exchange with a sucked by a fan and passed through the two-pass heat exchanger air flow of the ambient air.

When using multi-pass heat exchangers in frost-prone areas exists the risk that the multi-pass heat exchanger can not be emptied quickly enough and not completely, in order to prevent freezing of the heat transfer medium (in particular cooling water). Especially with a very rapid drop in temperature of located in the multi-pass heat exchanger heat transfer medium due to a rapid lowering of the ambient temperature or a strong wind influence on the heat exchanger must be ensured even when using multi-pass heat exchangers that the heat exchanger can be completely emptied within a very short time to prevent freezing of the heat transfer medium. However, a rapid emptying of a multi-pass heat exchanger is difficult due to the long pipes, which are repeatedly traversed by the heat transfer medium and the consequent long transport paths of the heat transfer medium through the pipes of the multi-pass heat exchanger. The length of the pipes (a return and return line) can be between 3 to 15 m. For the same reason, a quick refilling of a multi-pass heat exchanger at a resumption of the recooling operation after elimination of the risk of frost is difficult.

Proceeding from this, the present invention seeks to show a heat exchanger assembly with at least one multi-pass heat exchanger, which has a high cooling capacity at the highest possible efficiency and as quickly as possible and completely emptied at frost and for a resumption of a recooling after completion of the risk of frost again as possible can be filled quickly with a heat transfer medium.

These objects are achieved according to the invention with a heat exchanger assembly having the features of claim 1. To solve the problem also contributes to a cooling system according to claim 33, in which a heat exchanger assembly according to the invention is used as a recooler for cooling a fluid used as the heat transfer medium.

The heat exchanger arrangement according to the invention comprises at least one multi-pass heat exchanger, which comprises an outer inflow surface, which can be flowed by a gas flow, as well as a first distributor, a second distributor and at least one diverter distributor, and a plurality of conduits through which a fluid, in particular water, can flow. wherein the first manifold and the second manifold are disposed at one end of the heat exchanger assembly and the diverter manifold is disposed at the opposite end and the pipes extend from the one end to the opposite end and at least a portion of the piping communicates with the diverter manifold at a pipe end and at least a portion of the pipelines communicating with the diverter manifold are cranked at their manifold end facing the diverter manifold in a crimping area toward the diverter manifold. The Kröpfbereich is expediently bent away from the outer Anströmfläche inward.

By the bend of the pipes at their the diverter manifold facing the pipe end ensures that when emptying the heat exchanger assembly, which is necessary in particular at a risk of frost to prevent the guided in the pipes fluid freezes, the fluid completely from the Umlenkverteiler and in the piping can drain away without leaving any fluid residue in the diverter manifold which could freeze at outside temperatures below the freezing point of the fluid.

When emptying the heat exchanger assembly, the outflow of the fluid from the pipes is advantageously supported by a slope of the pipes to the horizontal plane. The angle of inclination is, for example, between 0.5 ° and 5 ° and preferably between 2 ° and 4 ° and in particular at 3 °.

For pressure equalization with the environment (ie with the atmospheric air pressure) is at least at one of the Umlenkverteiler, in particular at the first Umlenkverteiler and - in a 4-pass heat exchanger - preferably also on the second Umlenkverteiler, arranged a vent. The ventilation opening is expediently arranged at a highest point or near the highest point of the respective deflection distributor. Thereby, a complete ventilation of the Umlenkverteiler be guaranteed during emptying of the heat exchanger assembly, whereby the fluid flow is maintained at an emptying of the heat exchanger assembly. Accordingly, through the ventilation opening (s) causes a venting or deflecting distributor even with a filling of the heat exchanger assembly.

The Kröpfbereich the cranked pipes has away from the longitudinal axis of the pipes inwardly (thus directed away from the outer Anströmfläche) and has a Kröpfwinkel (α), preferably in the range of 5 ° to 90 ° and in particular in the range of 20 ° to 70 ° is. The crimp angle (α) can be different for the individual cranked pipes. In particular, the crimp angle (α) at (seen in the direction of flow of the gas stream) internal pipelines is smaller than at (on the inflow surface) external pipelines.

The Kröpfbereich is short compared to the length of the pipes and makes in particular at most 10%, preferably less than 5% and more preferably less than 1% of the length of the pipes.

The or each Umlenkverteiler is suitably tubular and formed the Umlenkverteiler facing pipe end of the cranked pipes opens at least approximately radially into the tubular Umlenkverteiler. As a result, an unhindered outflow of the fluid from the respective deflecting distributor can be ensured when the heat exchanger arrangement is emptied.

At the other, opposite pipe end, the pipelines are in communication with the first or the second distributor, wherein the other pipe end of the pipes preferably opens straight into the first or the second distributor in each case straight, and in particular radially or tangentially.

For supplying and discharging the fluid, a first connecting piece is arranged at a lowest point or at least near the lowest point of the first distributor, and a second connecting piece is arranged at a lowest point or at least in the vicinity of the lowest point of the second distributor. At the second manifold further, a third port is located at a highest point or at least near the highest point of the second manifold. When talking about a highest point of a distributor, it means the geodetically highest point of the respective distributor. When referring to a lowest point, it is meant the geodetically lowest point of each device (distributor), in particular the lowest point seen in relation to the vertical direction. In each case, a point is included, which is at least in the vicinity of the geodetically highest or the geodesic lowest point.

This preferred embodiment of the heat exchanger arrangement can be both rapid emptying and rapid filling of the multi-pass heat exchanger with the fluid used as heat transfer medium by the risk of gravity due to a tendency of the pipes to horizontal simultaneously from all pipes at risk of frost in a drain operation into the first and the second distributor and from there in each case via one at the lowest point of the first and the second distributor and (first or second connection nozzle) can flow into a communicating with the connecting piece fluid line. In a corresponding manner, in a filling operation, the fluid can be introduced very quickly against the force of gravity from the first and the second distributor into all the pipes of the multi-pass heat exchanger at the same time. This significantly shortens the emptying or the filling time when emptying or filling the heat exchanger, because the fluid is not introduced according to the flow paths in the recooling of the heat exchanger assembly in the multi-pass heat exchanger or, but on the first and the second distributor simultaneously in or from all the pipes of the multi-pass heat exchanger can flow.

In the multi-pass heat exchanger may be, for example, to a 2-pass heat exchanger in which the fluid flows twice through the pipes of the heat exchanger and thereby is in heat exchange with cooling air, suitably sucked by one or more fans from the environment and is passed through the heat exchanger.

The pipelines of each multi-pass heat exchanger are subdivided into a first and a second group of pipelines, the first group of pipelines serving as outgoing lines and the second group of pipelines as return lines. In the recooling operation, the fluid can be introduced, for example via the formed as an input manifold first connection piece in the first manifold and the fluid flows through the Hinleitungen (first group of pipes) of the 2-pass heat exchanger in a first pass to the first Umlenkverteiler and is from there into the Return lines (second group of pipes) deflected so that the fluid can then flow back in a second pass in the return lines to the second manifold (output manifold). The fluid leaves the two-pass heat exchanger over the third connection port arranged at the highest point of the second distributor. In this case, the two distributors (first distributor and second distributor) can also be interchanged with each other, that is, it is possible that the fluid first flows into the second distributor formed as an input distributor and flows out of the first distributor formed as an output distributor.

The multi-pass heat exchanger can also be a 4-pass heat exchanger, in which the fluid flows four times through the pipes of the heat exchanger and is in heat exchange with the cooling air. In a 4-pass heat exchanger, a second and a third deflection distributor is provided in addition to the first and the second distributor and the first Umlenkverteiler, wherein the first and the second distributor and the third Umlenkverteiler at one end of the heat exchanger assembly and the first and the second Deflection distributor are arranged at the opposite end of the heat exchanger assembly and the conduits extend from the one end to the opposite end for connecting the first and second distributors to one of the diverter manifolds. In this case, again at a lowest point or at least in the vicinity of the lowest point of the first distributor and the second distributor arranged a connecting piece (first and second connection piece) and on the second distributor is in turn a third connection piece at a highest point or at least in Located near the highest point of the second distributor. At the third deflecting distributor, a fourth connecting piece is expediently arranged at a lowest point or at least in the vicinity of the lowest point of the third deflecting distributor.

In the recooling operation of the 4-pass heat exchanger, the fluid can be introduced, for example, via the first connecting piece designed as an inlet manifold in the first manifold and the fluid flows through the Hinleitungen (first group of pipes) of the 4-pass heat exchanger in a first pass to the first Umlenkverteiler and is deflected from there into the return lines (second group of pipes), so that the fluid then flows back in a second pass in the return lines to the third diverter at the first end of the heat exchanger assembly and there from the third diverter again in pipelines of the first group (Hinleitungen ) is deflected and flows in a third pass to the second diverter manifold and there again in pipelines of the second group (return lines) is deflected to finally flow back in a fourth pass to the second manifold (output manifold). The fluid leaves the multi-pass heat exchanger over the third point at the highest point of the second manifold arranged. In this case, the two distributors (first distributor and second distributor) can also be interchanged with each other, that is, it is possible that the fluid first flows into the second distributor formed as an input distributor and flows out of the first distributor formed as an output distributor.

In order to ensure that the multi-pass heat exchanger is completely filled with fluid at all times during filling and during the recooling operation (whereby improved efficiency can be achieved), it is preferable for both the 2-pass and 4-pass heat exchangers the fluid enters the heat exchanger via the first connecting piece (at the lowest point of the first distributor) and leaves the heat exchanger at the second connecting piece (at the highest point of the second distributor).

The distributor, that is, the first and the second distributor as well as each deflection distributor, can each be designed as tubular multiple distributors. The tubes of the distributor can be arranged with its longitudinal axis vertical standing or inclined to the vertical. An inclination of the tubes of the or each deflecting distributor improves, in conjunction with the offset of the pipe ends which open into the deflecting distributor, the outflow of the fluid from the deflecting distributor when the heat exchanger arrangement is emptied and is therefore to be preferred. The inclination of Umlenkverteiler tubes with respect to the vertical plane is expedient in an angular range of 15 ° to 70 ° and preferably from 30 ° to 45 °.

A high heat exchange efficiency and a compact design of the heat exchanger assembly can be achieved if the heat exchanger assembly includes two oppositely arranged multi-pass heat exchanger, wherein the two multi-pass heat exchanger inclined to the vertical and V-shaped to each other standing. In accordance with this inclined arrangement of the heat exchangers, the tubular distributors (first distributor and second distributor as well as the deflecting distributor) also run obliquely to the vertical.

A particularly compact design can be achieved if the first and the second diverter are contained in a common manifold with a partition wall disposed therein, wherein the dividing wall, the common manifold into an inflow region, which forms the first manifold, and an outflow region, the second Distributor forms, divided. Correspondingly, in the 4-pass heat exchanger, the first and the second diverter manifold, which are respectively arranged adjacent to each other at the other end of the heat exchanger assembly, may be arranged in a common manifold with a partition, wherein the partition divides the manifold into at least two areas wherein a first region forms the first deflection distributor and a second region forms the second deflection distributor.

In a corresponding manner, in the 4-pass heat exchanger, the first distributor, the second distributor and the third deflection distributor, which are each arranged adjacent to one another at one end of the heat exchanger arrangement, can also be arranged in a common collecting tube, wherein the collecting tube in turn contains a separating element, which divides the manifold into at least an inflow region (forming the first manifold), an outflow region (forming the second manifold), and a deflection region (forming the third diverter manifold). In this case, the first, the second, the third and the fourth connecting piece are arranged in the common manifold, wherein the first connecting piece in the An inflow region at a lowest point of the common manifold, the second port in the outflow region at a highest point of the common manifold, the third port in the outflow region at a lowest point of the common manifold and the fourth port is located at a lowest point of the deflection.

Depending on the operating mode of the heat exchanger arrangement, the first and the second connection stubs and, if appropriate, the fourth connection stub which is provided at the lowest point of the distributor in question (first distributor and second distributor, possibly the third diverter distributor) to be able to open or close, preferably a controllable valve is assigned to each of these connecting pieces. The controllable valve can be arranged in particular in the respective connecting piece (first, second or fourth connection piece). The control of the controllable valves can be done for example hydraulically, pneumatically or electrically.

In an expedient embodiment of the heat exchanger arrangement, the first and the second distributors and (in the case of the 4-pass heat exchanger) the third deflecting distributor are arranged at a front end of the heat exchanger arrangement and the first deflecting distributor and possibly the (provided for 4-pass heat exchanger) second Umlenkverteiler are arranged on the opposite, rear end face of the heat exchanger assembly. In the case of the 4-pass heat exchanger, the third deflecting distributor is arranged adjacent to the first and second distributors on the front end side and the second deflecting distributor is adjacent to the rear deflecting distributor on the rear end side. As a result, a compact construction and a dimensioning of the heat exchanger arrangement corresponding to the requirements with regard to the cooling capacity can be ensured.

The heat exchanger arrangement according to the invention can be used in both the 2-pass and the 4-pass version in different operating modes, in particular in a recooling operation, a discharge operation at frost hazard, a filling operation for initial filling of the heat exchanger arrangement or for refilling after completion of the risk of frost as well be operated in a stand-by mode after a successful emptying of the heat exchanger assembly in case of danger of frost or in case of prolonged frost. For switching the heat exchanger arrangement from one operating mode to another operating mode, a control device for controlling the heat exchanger arrangement is provided. The control of the heat exchanger assembly, and in particular the adjustment of a suitable operating mode, is dependent on environmental parameters, e.g. the outside temperature and the wind speed at the installation of the heat exchanger assembly. To capture the environmental parameters are appropriate sensors, in particular a thermometer for detecting the outside temperature and an anemometer for detecting the wind speed, provided and coupled to the control device. The measured values of the environmental parameters detected by the sensors are supplied to the control device. In addition to the environmental parameters such as outside temperature and wind speed, the inlet temperature of the fluid upon entry into the heat exchanger arrangement is expediently detected via further sensors, in particular a thermometer. Furthermore, the volume flow of the fluid stream flowing into the heat exchanger arrangement or of the fluid flowing out of the heat exchanger arrangement can be measured by means of pressure or flow sensors and fed to the control device. On the basis of the supplied measured values, in particular taking into account the outside temperature and the inlet temperature of the fluid, the control device calculates a predicted outlet temperature of the fluid at the exit from the heat exchanger arrangement. If the calculated outlet temperature is greater than or equal to a predetermined limit, the controller switches the operation of the heat exchanger assembly from the recooling to the emptying mode. From the mathematically determined outlet temperature of the fluid at the exit from the heat exchanger arrangement, a freezing risk of the fluid can be detected at low outside temperatures below the freezing point of the fluid (which is preferably water). In order to prevent freezing of the fluid in the pipes or the distributors of the heat exchanger assembly in such a situation, the control device switches as quickly as possible in the emptying operation, in which the fluid located in the pipes simultaneously from all pipelines in the first and the second Distributor as well as the possibly existing (in 4-pass heat exchanger) third Umlenkverteiler and from there through the respectively at the lowest point of this manifold arranged connecting pieces (first, second and fourth connection piece) in a standing with these connecting piece fluid line from the frost-prone area can drain away.

• 1: Darstellung eines Ausführungsbeispiels einer erfindungsgemäßen Wärmeübertrageranordnung mit zwei V-förmig zueinander angeordneten 2-pass-Wärmeübertragern in einer Ansicht auf eine vordere Stirnseite der Wärmeübertrageranordnung;
• 2: Seitenansicht der 2-pass-Wärmeübertrageranordnung von 1;
• 3: Ansicht auf die hintere Stirnseite der 2-pass-Wärmeübertrageranordnung von 1;
• 4: Schematische Übersichts-Darstellung des Ausführungsbeispiels einer erfindungsgemäßen Wärmeübertrageranordnung der 1 bis 3 mit zwei V-förmig zueinander angeordneten 2-pass-Wärmeübertragern in einer Ansicht auf die vordere Stirnseite der Wärmeübertrageranordnung (4a), auf die hintere Stirnseite der 2-pass-Wärmeübertrageranordnung (4b) und in einer Seitenansicht ( 4c);
• 5: Schematische Darstellung verschiedener Betriebsmodi der 2-pass-Wärmeübertrageranordnung von 4, wobei in 5a ein Rückkühlbetrieb, in 5b ein Befüllungsbetrieb und in 5c ein Entleerungsbetrieb des 2-pass-Wärmeübertragers dargestellt ist;
• 6: Darstellungen der verschiedenen Betriebsmodi der 2-pass-Wärmeübertrageranordnung aus 4 anhand von Schnittzeichnungen des 2-pass-Wärmeübertragers durch eine horizontale Ebene, wobei in 6a der Rückkühlbetrieb, in 6b der Befüllungsbetrieb und in 6c der Entleerungsbetrieb des 2-pass-Wärmeübertragers dargestellt ist;
• 7: Schematische Darstellung eines Kühlsystems, welches eine erfindungsgemäße Wärmeübertrageranordnung mit zwei gegenüberliegenden 2-pass-Wärmeübertragern enthält, wobei in 7a das gesamte Kühl system und die darin eingesetzte Wärmeübertrageranordnung sowohl in einer Ansicht auf die vordere Stirnseite und in einer Seitenansicht gezeigt ist und 7b einen Detailausschnitt aus 7a im Bereich der Wärmeübertrageranordnung zeigt;
• 8: Schematische Darstellung verschiedener Betriebsmodi der Wärmeübertrageranordnung des Kühlsystems von 7, wobei 8a die Wärmeübertrageranordnung im Rückkühlbetrieb, 8b die Wärmeübertrageranordnung im Entleerungsbetrieb und 8c die Wärmeübertrageranordnung im Befüllungsbetrieb zeigt;
• 9: Schematische Darstellung eines weiteren Ausführungsbeispiels eines Kühlsystems mit einer Kombination von zwei Wärmeübertrageranordnungen gemäß der Erfindung;
• 10: Schematische Darstellung möglicher Betriebsmodi der Kombination von Wärmeübertrageranordnungen aus 9.

These and other features and advantages of the invention will become apparent from the embodiment described in more detail below with reference to the accompanying drawings. The drawings show:

• 1 : Representation of an embodiment of a heat exchanger arrangement according to the invention with two V-shaped mutually arranged 2-pass heat exchangers in one View on a front end side of the heat exchanger assembly;
• 2 : Side view of the 2-pass heat exchanger assembly of 1 ;
• 3 : View on the rear face of the 2-pass heat exchanger assembly of 1 ;
• 4 Schematic overview of the embodiment of a heat exchanger arrangement according to the invention 1 to 3 with two V-shaped mutually arranged 2-pass heat exchangers in a view of the front end side of the heat exchanger assembly ( 4a) , on the rear face of the 2-pass heat exchanger assembly ( 4b) and in a side view ( 4c) ;
• 5 : Schematic representation of various operating modes of the 2-pass heat exchanger assembly of 4 , where in 5a a recooling operation, in 5b a filling operation and in 5c a discharge operation of the 2-pass heat exchanger is shown;
• 6 : Representations of the different operating modes of the 2-pass heat exchanger arrangement 4 on the basis of sectional drawings of the 2-pass heat exchanger through a horizontal plane, in 6a the recooling operation, in 6b the filling operation and in 6c the discharge operation of the 2-pass heat exchanger is shown;
• 7 : Schematic representation of a cooling system, which contains a heat exchanger arrangement according to the invention with two opposite 2-pass heat exchangers, wherein in 7a the entire cooling system and the heat exchanger assembly used therein is shown both in a view of the front end side and in a side view, and 7b a detail from 7a in the area of the heat exchanger arrangement shows;
• 8th : Schematic representation of various operating modes of the heat exchanger assembly of the cooling system of 7 , in which 8a the heat exchanger arrangement in the recooling operation, 8b the heat exchanger assembly in the emptying operation and 8c shows the heat exchanger assembly in the filling operation;
• 9 : Schematic representation of another embodiment of a cooling system with a combination of two heat exchanger assemblies according to the invention;
• 10 : Schematic representation of possible operating modes of the combination of heat exchanger assemblies 9 ,

In the 1 and 2 an embodiment of a heat exchanger assembly according to the invention is shown, which can be used as a recooler R for cooling a fluid used as a heat transfer medium in a cooling system. In particular, water can be used as the heat transfer medium. When water is referred to in the following, the fluid used as the heat transfer medium is meant, wherein instead of water, another fluid can also be used as the heat transfer medium.

The in the 1 and 2 shown heat exchanger assembly includes two 2-pass heat exchanger, which contains opposing, oblique to the vertical, areal heat exchanger. The two heat exchangers are there, as from the view of 1 seen, V-shaped arranged to each other. Below we will see the construction of the on the left side of 1 arranged heat exchanger explained. The opposite, arranged on the right side of the heat exchanger assembly heat exchanger is constructed accordingly. The two heat exchangers are on a housing 21 attached to the heat exchanger assembly. Each heat exchanger comprises a first distributor 1 , which is designed as an input distributor, a second distributor 2 , which is designed as an output distributor, and a first Umlenkverteiler 4 and a plurality of pipelines 5 , The first distributor 1 and the second distributor 2 are doing at the front end face A arranged the heat exchanger assembly. The diverting distributor 4 is at the opposite end B the heat exchanger assembly, ie at the rear end, arranged. The pipelines 5 extend in a longitudinal direction L the heat exchanger assembly from the one end A to the opposite end B , The pipelines 5 are doing in a first group of pipelines 5a and a second group of pipelines 5b divided, with the first group of pipelines 5a as forward lines and the second group of pipelines 5b serve as return lines. The pipelines 5 the first group of pipelines 5a (Hinleitungen) connect the first distributor 1 (Input distributor) with the deflection distributor 4 the pipelines 5 the second group of pipelines 5b (Return lines) connect the Umlenkverteiler 4 with the second distributor 2 (Output distributor), as well as out 6 seen. The pipelines 5 the return and return lines run at least substantially parallel to each other and are slightly inclined to the horizontal, as shown in the 2 and 4c seen. The angle of inclination of the pipes 5 to the horizontal is preferably between 0.5 ° and 5 °, more preferably between 2 ° and 4 ° and in a preferred embodiment, the angle between the pipes and the horizontal plane is 3 °.

At the first distributor 1 (Input distributor) is at a lowest point T this distributor 1 a first connecting piece 1a arranged. At the appropriate place, ie, at a lowest point T, is also at the second distributor 2 (Output distributor) a second connection piece 2a arranged. At the second distributor 2 (Output distributor) is at a highest point H another connecting piece arranged as the third connecting piece 3 referred to as.

The one at the opposite end B the heat exchanger arrangement arranged Umlenkverteiler 4 has at a highest point H a ventilation opening 10 on, like out 2 seen. The ventilation opening 10 is expediently at the upper end of the designed as a tubular manifold manifold Umlenkverteilers 4 arranged. The opposite lower end of the tubular Umlenkverteilers 4 is closed. In every ventilation opening 10 is appropriate a valve 11 arranged with which the ventilation opening 10 can be opened or closed. In order to prevent that upon complete filling of the heat exchanger with the filled fluid, the fluid from the ventilation openings 10 can escape is in the vents 10 expedient a self-closing valve 11 arranged. The valve 11 closes the ventilation opening 10 automatically as soon as an internal pressure arises in the valve due to the incoming fluid. On the use of a valve in the ventilation holes 10 However, it can also be dispensed with if outflow of the fluid can be accepted with complete filling of the heat exchangers.

At least in the second connection piece 2a at the lower end of the second distributor 2 (Output distributor) is arranged, is a controllable (not shown here) valve for opening and closing the connection piece 2a used. Alternatively, this valve can also be placed at another location, for example in one with the second connection piece 2a related fluid line.

In 4 are an overview of the embodiment of the heat exchanger assembly according to the invention, the front end of the 2-pass heat exchanger assembly ( 4a) , the rear end face ( 4b) and a side view ( 4c) shown schematically. Out 4 In particular, the placement of the connection piece goes 1a . 2a and 3 at the first and at the second distributor 1 . 2 ( 4a) and the inclination of the arrangement and thus the running in the longitudinal direction L pipelines 5 to the front end A out ( 4c) ,

From the 5 and 6 show different operating modes of the heat exchanger assembly. In the in the 5a and 6a For example, water is used as the heat transfer medium through the pipelines 5 (outgoing lines 5a and returns 5b) passed the heat exchanger assembly. At the same time, at least one fan 12 disposed at the top of the heat exchanger assembly as shown in Figs 2 and 4c visible, (cold) ambient air sucked from the environment and passed through the heat exchanger of the heat exchanger assembly to heat exchange between the through the pipes 5 directed heat transfer medium (water) and the sucked air make. To increase the heat transfer efficiency are on the piping 5 slats 22 attached, like out 6 to detect, to increase the effective heat transfer area. Accordingly, in the exemplary embodiment shown, the heat exchangers are fin or fin tube heat exchangers. Instead of conventional finned or finned tube heat exchangers, microchannel heat exchangers can also be used in the heat exchanger arrangement according to the invention.

In the in the 5a and 6a The recooling operation shown schematically is the fluid used as the heat transfer medium via the first connecting piece 1a in the first distributor 1 (Input manifold) and then from there through the pipes 5 the first group of pipelines 5a (Hinleitungen) to Umlenkverteiler 4 passed and into the pipes of the second group of pipelines 5a (Return lines) redirected. The fluid flows through the return lines to the second manifold 2 (Outgoing distribution). The fluid is from the output manifold 2 through at the top of the output manifold 2 arranged third connection piece 3 removed and via a to the third connection 3 connected fluid line 9 as a cooling medium in a cooling medium reservoir (container B) or led directly to a consumer to be cooled.

In the recooling operation according to 5a and 6a is the second connection piece 2a closed by the valve disposed therein.

In the 5b and 6b the heat exchanger assembly is shown schematically in a filling operation, in which the heat exchanger either filled for the first time or can be refilled after emptying with the fluid. In the filling mode, the lower connection piece is 2a (second connection piece) of the second distributor 2 open. This allows the fluid to flow simultaneously over each at the bottom of the two manifolds 1 . 2 arranged connection piece 1a . 2a in the first and second distributor 1 . 2 be filled. The fluid then flows as in the 5b and 6b represented, simultaneously through all pipelines 5 (ie both by the fore-lines 5a as well as through the return lines 5b) in the same flow direction from the one end A of the heat exchanger assembly to the opposite end B , Due to the inclination of the pipes 5 towards the front end A, the fluid flows in the pipelines 5 doing against the force of gravity upwards in the direction of the rear end face B arranged Umlenkverteilers 4 , It will be in the Umlenkverteiler 4 air through the ventilation opening 10 at the upper end of the Umlenkverteilers 4 pushed out, causing the Umlenkverteiler 4 is vented. In order to prevent that upon complete filling of the heat exchanger with the filled fluid, the fluid from the vent 10 can escape is in the vent 10 expedient a self-closing valve 11 arranged. The valve 11 closes the ventilation opening 10 automatically as soon as an internal pressure arises in the valve due to the incoming fluid.

In accordance with the filling of the heat exchanger arrangement with the fluid can conversely by opening the valve in or on the second connection piece 2a also a quick emptying of the heat exchanger arrangement done. In the 5c and 6c a discharge operation of the heat exchanger assembly is shown in the valve with the valve open in the second connection 2a the fluid at the same time from all pipelines 5 (ie both from the fore-lines 5a as well as from the return lines 5b) Due to gravity and in the same flow direction along the slope of the pipes 5 from the back end B to the front end A towards the first and the second distributor 1 . 2 can flow. The flow of the fluid is on the one hand by the inclination of the pipes 5 to the front end A on the other hand by a ventilation of Umlenkverteilers 4 over the ventilation opening 10 promoted. For ventilation of the diversion manifold 4 becomes the valve 11 in the vents 10 open, allowing ambient air through the vent 10 in the deflection manifold 4 can flow in. The fluid can eventually pass through the lower spigot 1a . 2a (First, and second connecting piece) flow into a fluid line, not shown here, which with these connecting pieces 1a . 2a communicates.

The inventive design of the heat exchanger can be both rapid filling with the fluid and (in case of frost) rapid emptying of the heat exchanger arrangement, because the fluid both during filling and during emptying simultaneously and each in the same flow direction through all pipeline 5 the heat exchanger arrangement can flow in or out.

When emptying the heat exchanger assembly can as complete as possible emptying of the heat exchanger and in particular the Umlenkverteilers 4 by a bend of the pipes 5 at its pipe end, which in the Umlenkverteiler 4 leads to be achieved. The bend of the pipes 5 at the in the Umlenkverteiler 4 opening pipe end 5 ' comes from 6 out. As in 6 is shown in the diverter 4 opening pipe end 5 ' part of the piping 5 in the direction of the diversion manifold 4 out in one (compared to the total length of the piping 5 ) short bend area 6 cranked. In this case, the Kröpfbereich of the outer Anströmfläche F away inside, like out 6 can be seen in the left heat exchanger from the heat exchanger assembly of 1 to 3 is shown. The crotch area 6 points for the individual pipelines 5 an at least partially different crimp angle α. The crimp angle α, below which the crimping area 6 is bent away from the longitudinal axis, is expediently between 5 ° and 90 ° and in particular in a Kröpfwinkelbereich of 20 ° ≤ α ≤ 70 °. How out 6 the crimp angle (α) is visible at (in the flow direction of the gas flow flowing from the inflow surface F through the heat exchanger) internal pipelines (in the example shown, these are the forward lines 5a) is smaller than in the more external pipelines (ie the inflow facing pipelines, here the return lines 5b) ,

By the bend of a part of the pipes 5 at her the Umlenkverteiler 4 facing pipe end 5 ' the cranked pipes open 5 at least approximately radially in the tubular deflecting distributor 4 , As a result, an unhindered outflow of the fluid from the Umlenkverteiler 4 especially when emptying the heat exchanger arrangement allows. An unhindered outflow of the fluid from the Umlenkverteiler 4 on the one hand provides a quick and on the other hand also a complete emptying of Umlenkverteilers 4 for sure. For a complete emptying of Umlenkverteilers 4 can also be an inclination of the tube of Umlenkverteilers 4 contribute in relation to the vertical plane, because in this case, the fluid disability-free from the oblique Umlenkverteiler 4 down into the crotch area 6 the with the diverter 4 related, cranked pipelines 5 can drain away. Due to the inclination of the Umlenkverteilers 4 also runs on the pipe of Umlenkverteilers 4 fortified crotch area 6 the cranked piping 5 obliquely to the horizontal plane, creating a unhindered fluid drain into the piping 5 is supported.

The crimping area 6 opposite, other pipe end 5 ' the piping 5 , which with the first or the second distributor 1 . 2 communicates expedient straight (ie without cranking) either centrally on the central longitudinal axis of the respective distributor 1 . 2 (and thus radially in the distributor) or offset to the central longitudinal axis (and thus tangential) in the respective distributor 1 . 2 a, like in 6 shown.

In 7 For example, a cooling system is shown in which a heat exchanger arrangement according to the invention can be used. This in 7 schematically shown cooling system comprises a circuit K , in which a fluid, in particular water, is guided as a heat transfer medium, one with the circuit K related containers B in which the fluid is stored, a heat source Q , which supplies heat to the fluid at the location of the heat source, as well as at least one heat exchanger arrangement according to the invention, which in the cooling system as a recooler R is used to cool the fluid by heat exchange with the ambient air. In the in 7 the example shown, the heat exchanger assembly with two 2-pass heat exchangers according to the 1 to 3 used as a recooler R.

The recooler R of the cooling system stands on fluid lines 9 with the container B in connection. The container B is preferably open to the environment of the container location. From the container B leads a fluid line 19 to the heat source Q to the stored and cooled in the container B fluid as a cooling medium to the heat source Q respectively. To convey the fluid from the container B to the heat source Q is a first pump P1 intended. At the place of the heat source Q the fluid is heated by heat exchange and by another line 29 back to the recooler R directed. It is useful in the line 29 a second pump P2 arranged, which the fluid from the heat source Q back to the recooler R promotes. From the line 29 branches a branch line 30 in the container B from. For opening and closing the branch line 30 is a valve V4 intended. Another valve V3 is downstream of the branch line 30 in the pipe 29 arranged. The administration 29 branches at a branch office Z in a return line 31 to the container B and in one to the recooler R leading supply line 32 , In the return line 31 is to open and close this line another valve V2 arranged. The supply line 32 branches into a central supply line and two secondary lines, each containing a three-way valve V1 is arranged. The central supply line branches again into two branches, wherein a first branch with the first connecting piece 1a the left heat exchanger and a second branch with the first connection piece 1a the right heat exchanger communicates. The secondary lines lead to the second connection 2a the left and right heat exchanger, as out 7b seen. The supply line 32 thus stands over the three-way valves V1 with the lower connecting pieces 1a and 2a the heat exchanger assembly in conjunction. To the (upper) third connection piece 3 the heat exchanger assembly is a discharge line 33 connected, which to the line 9 leads and communicates with it.

Out 8th go from different operating modes of the heat exchanger assembly in the cooling system of 7 out. In this case, the fluid is dashed in the hot state and characterized in the cold state with a solid line. In a dotted line no fluid flow takes place.

In 8a is the cooling system of 7 shown in the recooling mode. Here are the valves V2 and V4 closed, so that the wires 30 and 31 are closed. The valve V3 is open, so that from the heat source Q heated fluid through the lines 29 and 32 to the recooler R can flow. The three-way valves V1 are closed, leaving the fluid from the line 32 each to the first connection piece 1a of the first distributor 1 (Input manifold) of the two multi-pass heat exchanger flow and thereby can enter the heat exchanger assembly. After repeated passage of the fluid through the multi-pass heat exchanger of the recooler R the cooled fluid leaves the recooler R on the third connection piece 3 and flows through the at the third connection nozzle 3 connected line 33 to the line 9 and from there into the container B in which the cooled fluid is stored.

In the in 8b shown draining operation are the valves V2 and V4 opened and valve V3 is closed. The three-way valves V1 are switched so that the fluid from the lower connecting pieces 1a . 2a (first and second connection piece) in the fluid line connected to this connection piece 9 and from there directly into the container B can flow. While emptying the recooler R it gets from the heat source Q heated fluid via the branch line 30 with the valve open V4 in the container B returned without the fluid through the recooler R to be led.

In the in 8c shown filling operation are the valves V2 and V4 closed and the valve V3 is open. The three-way valves V1 are controlled so that that of the heat source Q heated fluid over the lines 29 and 32 to the lower connecting pieces 1a . 2a (first and second connecting piece) of the multi-pass heat exchanger is passed and from there into the recooler R entry. After complete filling of the heat exchanger of the recooler R is the recooler in the recooling operation ( 8a) switched.

In 9 an embodiment of a cooling system is shown, in which two heat exchanger arrangements according to the invention as a recooler R1 . R2 can be used in parallel or series operation. The two recoolers R1 . R2 can be used, for example, in series or in parallel at the same time for cooling the fluid used as the heat transfer medium in the cooling system. With simultaneous use of both recoolers R1 . R2 a maximum cooling capacity of the cooling system is achieved. If a lower cooling capacity is needed for a sufficient cooling of the fluid, one of the two recoolers R1 or R2 by the control device S of the cooling system.

In parallel operation, in which both recoolers R1 . R2 are operated simultaneously to cool the fluid, the valves V2 and V4 closed and the valve V3 is open, so that from the heat source Q heated fluid in the two recoolers R1 . R2 in each case through the first connecting piece 1a can be initiated. That in the recoolers R1 . R2 cooled fluid leaves the recooler R1 . R2 each at the third connection piece 3 and flows through the with the third connection piece 2a connected fluid line 9 in the container B (as in 9 shown).

In the in 10a shown operating mode of the cooling system of 9 are the valves V3 and V4 closed and valve V2 is open. This will only be the second recooler R2 operated in the recooling mode. The first recooler R1 is in a stand-by mode where there is no fluid through the pipes of the first recooler R1 is directed.

In the in 10b shown operating mode is the second recooler R2 with the valve open V3 and closed valves V2 and V4 operated in the recooling mode, in which the from the heat source Q heated fluid through the first spigot 1a in the heat exchanger of the second recooler R2 introduced and cooled there and finally through the second connecting piece 2a from the second recooler R2 via the to the third connection piece 3 connected fluid line 9 led out and into the container B is passed. At the same time, the first recooler R1 operated in the filling operation, in which the fluid through the first connecting piece 1a and the second connecting piece 2a the heat exchanger at the same time in all pipelines 5 of the first recooler R1 is introduced to the recooler R1 completely filled with fluid.

To control the heat exchanger arrangement according to the invention in the various operating modes, a plurality of sensors is expediently provided S1 . S2 used with which environmental parameters, such as the outside temperature ( T _U ) and / or the wind speed (v) can be detected and passed to a control device S for processing. In addition to the environmental parameters are useful over other sensors T1 . T2 , P the inlet temperature ( T _a ) of the fluid entering the heat exchanger assembly, the temperature of the fluid in the diverters 4 . 6 and the pressure or flow rate of the fluid entering the inlet manifold 1 detected.

Those in the scheme of the cooling system of 7a designated by reference numeral S control means is to the valves V . V1 . V2 . V3 and V4 coupled to control these. The ones from the sensors S1 . S2 ; T1 . T2 . P measured values are passed to the control device and the control device calculates an outlet temperature based on the measured values ( T _off ) of the fluid upon exiting the heat exchanger assembly. When calculating the value of the outlet temperature ( T _off ), the parameters of the heat exchanger assembly, in particular their thermal performance, the dimensioning of the heat exchanger, the number of passes of the fluid through the pipes, the fluid used as the heat transfer medium and the volume flow of the fluid through the pipes, taken into account (maximum) cooling to determine the fluid when emptying the heat exchanger assembly. The control device controls the valves of the heat exchanger arrangement such that the heat exchanger arrangement is operated in the recooling mode, as long as the calculated outlet temperature ( T _off ) greater than or equal to a predetermined limit ( T _min ). Once the calculated exit temperature ( T _off ) falls below the limit (ie at T _off < T _min ), the heat exchanger assembly is switched to the discharge operation. The switching takes place, for example, by electrical or pneumatic actuation of the valves V . V1 . V2 . V3 and V4 ,

The default limit ( T _min ) is expediently a value Δ above the freezing point of the fluid used as the heat transfer medium (in the case of water, therefore, above 0 ° C.), the value Δ representing a safety distance from the freezing point.

Thus, even with a fast emptying ensures that the fluid does not freeze at frost hazard. Preferably, the value .DELTA. (And thus at Use of water as heat transfer medium the limit T _min = 0 ° C + Δ) between 1 ° C and 7 ° C.

After complete emptying, the heat exchanger assembly is left in a standby mode in which the heat exchangers are not filled with fluid. In the stand-by mode, it is monitored whether the risk of frost has been eliminated or still exists by calculating the progonisted outlet temperature (FIG. T _off ) and compared with the limit. Once the calculated exit temperature ( T _off ) greater than or equal to the predetermined limit value ( T _min ), the control device switches the heat exchanger arrangement from the stand-by to the filling operation. After complete filling of the heat exchanger arrangement, this is switched to the recooling operation and operated until the calculated outlet temperature ( T _off ) is below the threshold.

In the embodiment of 9 the heat exchanger arrangement comprising a plurality of heat exchangers is controlled by the control device in such a way that the individual multi-pass heat exchangers can be operated independently of one another in the different operating modes. In this case, the control device controls the number of heat exchangers operated in the recooling operation as a function of the detected environmental parameters and / or the detected inlet temperature ( T _a ) of the fluid in order to provide a required cooling capacity can. The per volume of time passed through the heat exchanger assembly fluid volume remains suitably equal regardless of the number of operated in the recooling heat exchanger. In this case, the control device monitors whether the temperature of the cooled in the heat exchanger assembly and stored in the container fluid is in a preferred temperature range between a minimum and a maximum temperature. The preferred temperature range of the fluid stored in the container B may be, for example, between 15 ° C and 22 ° C.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• WO 2018/184908 A1 [0003]
• WO 9015299 [0005]

Claims (35)

Heat exchanger arrangement with at least one multi-pass heat exchanger, which has an outer inflow area (F) which can be flowed by a gas flow, as well as a first distributor (1), a second distributor (2) and at least one diverter distributor (4), and a plurality of pipelines (5). comprises, which of a fluid, in particular water, can be flowed through, wherein the first distributor (1) and the second distributor (2) at one end (A) of the heat exchanger assembly are arranged and the Umlenkverteiler (4) at the opposite end (B) and the pipes (5) extend and of which one end (a) to the opposite end (B) at least a part of the pipes (5) on a tube end (5 ') to the turning manifold (4) is connected, characterized in that at least a part of the pipelines (5), which are in communication with the deflecting distributor (4), are arranged at their pipeline end (5 ') facing the deflecting distributor (4) m Kröpfbereich (6) to the deflection manifold (4) is cranked. Heat exchanger arrangement according to Claim 1 , wherein the Kröpfbereich (6) of the outer Anströmfläche (F) is bent inwardly away. Heat exchanger arrangement according to Claim 1 or 2 characterized in that the crimping region (6) is offset away from the longitudinal axis of the conduits (5) by a crimp angle (α), the crimp angle (α) being in the range of 5 ° to 90 ° and in particular in the range of 20 ° to 70 °. Heat exchanger arrangement according to Claim 3 in which the crimp angle (α) is smaller in the case of internal pipes (5b, 5c) located in the direction of flow (v) of the gas flow than in the case of external pipes (5e, 5f). Heat exchanger arrangement according to one of the preceding claims, wherein the Kröpfbereich (6) compared to the length of the pipes (5) is short and in particular at most 10%, preferably less than 5% and more preferably less than 1% of the length of the pipes (5) accounts. Heat exchanger arrangement according to one of the preceding claims, wherein the Umlenkverteiler (4) is tubular and the Umlenkverteiler (4) facing the pipe end (5 ') of the pipes (5) at least approximately radially into the tubular Umlenkverteiler (4) opens. Heat exchanger arrangement according to one of the preceding claims, wherein the pipes (5) at the other pipe end (5 ") with the first or the second distributor (1, 2) are in communication. Heat exchanger arrangement according to Claim 7 , characterized in that the other pipe end (5 ") of the pipes (5) opens straight into the first or the second distributor (1, 2). Heat exchanger arrangement according to Claim 8 , wherein the first and the second distributor (1, 2) are each tubular and the other pipe end (5 ") of the pipes (5) opens either radially or tangentially into the tubular distributor (1, 2). Heat exchanger arrangement according to one of the preceding claims, characterized in that the first distributor (1) has a first connection piece (1a) for connection to a fluid line (9), and the second distributor (2) has a second connection piece (2a) for connection to a fluid line (9 '), wherein the first port (1a) at a lowest point (T) or at least near the lowest point (T) of the first manifold (1) and the second port (2a) at a lowest point (T ) or at least in the vicinity of the lowest point (T) of the second distributor (2) is arranged. Heat exchanger arrangement according to one of the preceding claims, characterized in that at the first distributor (1) and / or at the second distributor (2) a third connecting piece (3) at a highest point (H) or at least near the highest point (H) of the respective distributor (1 and / or 2) is arranged. Heat exchanger arrangement according to one of the preceding claims, characterized in that the heat exchanger has an outer inflow area (F) which can be flowed by a gas flow, wherein the distributor (1, 2), which faces the inflow area (F), has the third connection stub (3). contains. Heat exchanger arrangement according to one of the preceding claims, characterized in that at a highest point (T) or at least in the vicinity of the highest point (T) of Umlenkverteilers (4) at least one vent opening (10) is arranged for pressure equalization with the environment. Heat exchanger arrangement according to Claim 13 , characterized in that in the ventilation opening (10) a valve (11) having a predetermined maximum flow cross-section (d) for the passage of air is arranged, wherein the valve (11) can be opened and closed and at complete opening of the valve (11), the maximum flow cross-section (d) for the passage of air is free and the valve (11) automatically closes when the fluid enters the valve (11). Heat exchanger assembly according to one of the preceding claims, wherein the pipes (5) of a first group of pipes as Hinleitungen (5a) formed and connected to the first manifold (1) and the Umlenkverteiler (4) and the pipes of a second group of pipes as return lines (5b) are formed and connected to the second distributor (2) and the Umlenkverteiler (4). Heat exchanger arrangement according to one of the preceding claims, characterized in that the pipes (5) are inclined to the horizontal by an inclination angle, wherein the Hinleitungen (5a) from the first distributor (1) to Umlenkverteiler (4) relative to the horizontal rise and the return lines (5b ) from the deflecting distributor (4) to the second distributor (1) fall off. Heat exchanger arrangement according to one of the preceding claims, wherein the first manifold (1), the second manifold (2) and the Umlenkverteiler (4) each formed as a tubular manifold, which is preferably arranged so that its longitudinal axis is vertical or inclined at an angle to the vertical is. Heat exchanger arrangement according to one of Claims 10 to 17 , characterized in that the first connection piece (1a) and / or the second connection piece (2a) is assigned a controllable valve. Heat exchanger arrangement according to one of Claims 16 to 18 , wherein the angle of inclination, which include the pipes (5) with the horizontal, between 0.5 ° and 5 ° and particularly preferably between 2 ° and 4 °. Heat exchanger arrangement according to one of the preceding claims, characterized in that in a discharge operation, the fluid from all pipelines (5) flows by gravity into the first distributor (1) and the second distributor (2) and that in a filling operation the fluid against gravity from the first distributor (1) and the second distributor (2) flows into the pipes (5). Heat exchanger arrangement according to one of Claims 16 to 19 , characterized in that in a recooling operation, the fluid flows through the first connecting piece (1 a) in the forward lines (5 a) and flows through the third connecting piece (3) from the return lines (5 b). Heat exchanger arrangement according to one of the preceding claims, characterized in that the fluid in the emptying operation by gravity flows through the first connection piece (1a) of the first distributor (1) and the second connection piece (2a) of the second distributor (2) into a lower fluid line (9) , which communicates with the first and the second connection nozzle (1a, 2a). Heat exchanger assembly according to one of the preceding claims, wherein the heat exchanger assembly comprises two oppositely disposed heat exchanger, each inclined to the vertical and V-shaped to each other. Heat exchanger assembly according to one of the preceding claims, wherein the fluid passes through the pipes (5) of each heat exchanger two or four times. Heat exchanger arrangement according to one of the preceding claims, wherein each heat exchanger in addition to the first Umlenkverteiler (4) comprises a second Umlenkverteiler (6) and a third Umlenkverteiler (8), wherein one of the Umlenkverteiler (8) at the end (A) of the heat exchanger is arranged where the first and second distributors (1, 2) are located. Heat exchanger arrangement according to one of the preceding claims, characterized by a plurality of sensors for detecting environmental parameters, in particular the outside temperature and / or the wind speed. Heat exchanger arrangement according to one of the preceding claims, wherein the Umlenkverteiler (4) is tubular and arranged so that its longitudinal axis is inclined to the vertical, preferably at an angle in the range of 15 ° to 70 °, in particular from 30 ° to 45 °. Heat exchanger arrangement according to one of the preceding claims, wherein the heat exchanger arrangement in response to ambient parameters, in particular the outside temperature, in a recooling operation, a discharge operation or a filling operation is operable, and the fluid in the recooling operation via the first connecting piece (1a) at the lowest point (T ) or at least in the vicinity of the lowest point (T) of the first distributor (1) introduced into the heat exchanger assembly and via the third connecting piece (3) at the highest point (H) or at least in the vicinity of the highest point (H) of the second Distributor (2) is derived that in the emptying operation, the fluid from all ducts (5) in the first distributor (1) and the gravitational second manifold (2) and from there in each case via a at the lowest point (T) or at least in the vicinity of the lowest point (T) of the first manifold (1) and the second manifold (2) arranged connecting piece (1 a, 2 a) in a fluid line (9) flows away, wherein in the filling operation, the fluid against gravity from the first manifold (1) and the second manifold (2) flows into all the pipes (5). Heat exchanger arrangement according to one of the preceding claims, characterized in that in the ventilation opening (10) of the first Umlenkverteilers (4) a valve (11) having a predetermined maximum flow cross-section (d) is arranged for the passage of air, wherein the valve (11) is opened and when the valve (11) is completely open, the maximum flow cross-section (d) for the passage of air is released and the valve (11) automatically closes when the fluid enters the valve (11). Heat exchanger assembly according to one of the preceding claims, wherein the heat exchanger assembly comprises two oppositely disposed heat exchanger, each inclined to the vertical and V-shaped to each other. Heat exchanger assembly according to one of the preceding claims, wherein the fluid passes through the pipes (5) of each heat exchanger two or four times. Heat exchanger arrangement according to one of the preceding claims, wherein each heat exchanger in addition to the first Umlenkverteiler (4) comprises a second Umlenkverteiler (6) and a third Umlenkverteiler (8), wherein one of the Umlenkverteiler (8) at the end (A) of the heat exchanger is arranged where the first and second distributors (1, 2) are located. Cooling system comprising - a circuit (K) in which water is passed as a heat transport medium, - a container (B) in communication with the circuit (B), in which the water is stored, - a heat source (W), which the fluid supplying heat at the location of the heat source, - and a recooler (R) in which the water is cooled by heat exchange with the ambient air, characterized in that the recooler (R) at least one heat exchanger assembly (1) according to one of the preceding claims. Cooling system after Claim 33 characterized by a control device for controlling the heat exchanger arrangement, wherein the heat exchanger arrangement can be operated via the control device as a function of ambient parameters, in particular the outside temperature and / or the wind speed, in a recooling operation, a discharge operation or a filling operation. Cooling system after Claim 34 , Characterized in that the environmental parameters, in particular the ambient temperature (Tu) and / or the wind speed (v), and the inlet temperature are detected (T _a) of the fluid entering the heat exchanger arrangement by means of sensors and fed as measured values to a control device and that the control device for calculating an outlet temperature (T _out ) of the fluid at the exit from the heat exchanger arrangement is set up on the basis of the detected measured values and operates the heat exchanger arrangement in the recooling mode, as long as the calculated outlet temperature (T _out ) is greater than or equal to a predetermined limit value and the heat exchanger arrangement in switches over the emptying mode when the calculated outlet temperature (T _out ) is below the limit value.

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