EP3102903A1

EP3102903A1 - Heat exchanging device

Info

Publication number: EP3102903A1
Application number: EP14816136.7A
Authority: EP
Inventors: Frank Günter LEHMANN
Original assignee: Hydac Cooling GmbH
Current assignee: Hydac Cooling GmbH
Priority date: 2014-02-08
Filing date: 2014-12-19
Publication date: 2016-12-14
Anticipated expiration: 2034-12-19
Also published as: BR112016017371A2; US20160341482A1; US10295264B2; CN106133471A; BR112016017371B1; DE102014001703A1; WO2015117635A1; ES2699881T3; EP3102903B1; DK3102903T3; CN106133471B

Abstract

A heat exchanging device (2), in particular a fluid/air heat exchanger, having individual fluid-conducting collecting chambers (6, 10) which in each case have an inlet (8) or outlet (12) for fluid supply and discharge and which are connected to one another via duct-like fluid guides (14) which control the temperature of, in particular cool, a fluid flow during operation of the device by means of an air flow which flows in duct-like air guides which are separated from the fluid guides (14) in a medium-tight manner, is characterized in that, in order to construct the overall heat exchanging device (2), at least one further collecting chamber (18; 20, 22) is inserted between collecting chambers (6, 10) which are arranged on outer sides which lie opposite one another, which further collecting chamber (18; 20, 22) is arranged parallel to the collecting chambers (6, 10) which lie on the outside, and into which further collecting chamber (18; 20, 22) all the fluid guides (14) which are connected to a collecting chamber (6, 10) which lies on the outside likewise open.

Description

Heat exchange device

The invention relates to a heat exchange device, in particular fluid-air heat exchanger, with individual fluid-carrying collecting chambers, each having an input or output for the Fluidzu- or -abfuhr and are connected to each other via channel-like fluid guides, which means a fluid flow during operation of the device a temperature of air flow, in particular cooling, which flows in channel-like air ducts, which are separated media-tight from the fluid guides.

Heat exchange devices of this type, also called lamella coolers, are state of the art. With air as the cooling medium, such heat exchangers are often used for cooling hydraulic fluids for the working hydraulics of mechanical systems, such as construction machinery or the like, for hydrostatic drives or as oil cooler for heavy-duty gearbox, especially in wind turbines. The document DE 10 2010 056 567 A1 shows an example of the use of such a heat exchanger in a liquid-air cooling system for generating a cooling capacity for the hydraulic fluid in the hydraulic working circuit of an associated machine unit. In operation of such systems, the heat exchangers are not only exposed to mechanical stresses, but due to the wide range of temperatures that can occur at the system components in operation, especially thermal loads. Such loads arise both due to the operating temperatures of the media involved, such as air and fluid, as well as due to the influences of ambient temperatures at the site of the heat exchanger, for example, due to the climatic conditions at the site. In heat exchangers in the form of so-called. Lamellenkühlern in conventional construction, which, as shown in DE 10 2010 046 91 3 A1, are constructed of a package of superimposed plates between which channel-like air ducts and fluid guides are formed in alternation, it may, for example high operating temperatures of the fluids due to temperature jumps, such as occur in intermittent operation, come due to elongation to tensions in the package of components. Possible consequences are stress cracks in the package connected by soldering to a rigid block, in particular in the area of the soldered seams, with the risk of failure of the heat exchanger and thus the danger of the associated system. To avoid this, it is known from the mentioned DE 10 2010 046 913 AI to give the solder pads on the plates forming strips a special profile shape, which leads to an approximately linear change in the flexural strength of the legs of the profile, so that an optimal bending behavior of Thigh reached and the risk of stress cracking at the soldering areas is minimized.

While the danger of malfunctions in temperature jumps over such high temperature ranges is effectively avoided, problems may arise due to low, occurring at the heat exchanger temperatures. This is particularly the case when the corresponding systems are used in harsh climates, for example in northern areas of the USA, in Canada, northern China or similar areas and when the systems are directly exposed to environmental influences such as wind turbines. The viscosity changes of the fluid, as they occur in winter operation at low temperatures, lead to pressure drops. Paraffin formations which can occur in the fluids at low temperatures. In order to make the fluid-air cooling systems suitable for winter use, the heat exchangers in question are usually designed in larger material thicknesses and / or the amount of cooling air is reduced by the speed variance of the associated fan, for example by means of control systems as described in the already mentioned document DE 10 201 056 567 A1.

In view of this problem, the invention has for its object to provide a heat exchange device of the type considered available, which is characterized by an improved operating behavior in the low temperature range.

According to the invention this object is achieved by a heat exchange device having the features of claim 1 in its entirety.

An essential feature of the invention is accordingly that of which the temperature is to be fluid leading plenums, each having a fluid input or output, three or more collecting chambers are provided which, based on the input to output ver ^¬ current flow direction, parallel are arranged to each other. Compared to the usual construction, in which the heat exchanger is flowed through over the entire length between the two end-side collecting chambers extending fluid channels, halve in the invention with at least one disposed between end collecting chambers further collecting space both the run length and the volume flow per collection room. The operating pressure loss is thus reduced to a quarter of the usual value, with corresponding improvement in the operating behavior at low temperatures with the associated changes in viscosity. The aspired winter suitability can be achieved without larger wall thicknesses and also at high air flow, so that simpler fan drives can be used and thereby result in a significantly reduced overall manufacturing costs.

The construction of the device can advantageously be such that a collecting space with an inlet or outlet for fluid is arranged centrally between two groups of channel-like fluid guides separated from one another via this collecting space, which open out at their mutually remote free ends into an outer collecting space which has an output or an input.

Likewise, the heat exchange device can be constructed from at least two fluid-air heat exchangers, which, preferably arranged in one plane, with their adjacent collecting chambers in a common fluid flow Direction, have an input or output, which via the channel-like fluid guides each connected collecting spaces form the output or input for the fluid. In such a designed embodiment with at least two fluid-air heat exchangers, of which a collecting space of a heat exchanger at opposite end portions has an input and an output, this can be connected in a series arrangement to the input of the next collecting space of another heat exchanger.

In this case, the collecting chambers connected to one another in a series arrangement may have an opposite direction of flow during operation of the device, wherein the further collecting space of the second heat exchanger connected to the one heat exchanger in a series arrangement is connected with its output to the inlet of the collecting space of the one heat exchanger its other, opposite end has an output. Again, this run lengths of the fluid channels and the flow rates within the Halves halved. In embodiments with two or more fluid-air heat exchangers, these can be arranged in desired spatial allocations relative to each other, so that the overall device is easily adaptable to given installation situations. For a particularly favorable operating behavior in the low temperature range, each of the heat exchangers used in each case can be chosen in terms of volume equal in size to achieve the same optimum flow conditions in all collecting spaces.

Furthermore, the arrangement may advantageously be such that the channel-like fluid ducts flow into the collecting space over the entire overall height or structural length of a collecting space designed in the manner of a collecting tank, the air flow of which takes place during operation of the apparatus essentially transversely to the fluid guide in the connected collecting space ,

In order to increase the air throughput for efficient heat exchange, in particular cooling, an associated fan device may preferably be arranged on the front side of the channel-like fluid guides.

The invention with reference to embodiments shown in the drawings will be explained in detail. Show it:

1 in the manner of a highly schematically simplified functional sketch, which only illustrates the course of the fluid flow, a heat exchange device according to the prior art;

Fig. 2 in Fig. 1 corresponding representation a modified

Heat exchange device according to the prior art; Fig. 3 in Figures 1 and 2 corresponding schematic representation of the heat exchange device according to a first embodiment of the invention. and

Fig. 4 to 7 in a corresponding representation of a heat exchanger

Heat exchange device according to a second or third or fourth or fifth embodiment of the invention.

The figures show of air-fluid heat exchangers in the form of plate coolers, also called lamella cooler, only collecting spaces with Fluidein- and / or fluid output and clear only with flow arrows clarified fluid flow path between collecting. The structural details of the fluid guides for the fluid flow between collecting chambers as well as the details of the air ducts extending transversely to the fluid guides are omitted in the simplified sketch figures. As an example of a related, specific construction of a corresponding plate package with extending between the plates, channel-like fluid and air guides reference is made to the already mentioned document DE 10 2010 046 913 A1.

Fig. 1 shows a heat exchange device 2 according to the prior art with a fluid collecting chamber 6 with a fluid inlet 8 and a collecting space 10 with a fluid outlet 12. The collecting spaces 6 and 10 are box-shaped with preferably rectangular cross-section and on two opposite outer sides arranged the heat exchanger. In this case, the collecting chambers 6,10 extend over the entire height of the plate package and over the plane perpendicular to the drawing level dimension, so that all fluid guides 14 open out with the unnumbered flow arrows in the plenums 6 and 10, wherein the direction of flow from the entrance 8 having collecting space 6 to the collection chamber 10 with the output 12 runs. Fig. 2 shows another embodiment of the prior art, in turn, the fluid guides 14 extend over the entire length of the distance between outer collecting spaces, wherein, in contrast to Fig. 1, however, the left-side collecting space 6 is only over half Height of the package extends and this collection space 6 another collecting space 16 connects, on which the fluid outlet 12 is provided. During operation, therefore, this heat exchange device 2 flows through between the collecting chambers 6 and 16 located on the left outside and the opposite collecting chamber 10 located on the outside in a first flow direction and in a second flow direction.

Fig. 3 shows a first embodiment of a heat exchanger of the heat exchange device 2 according to the invention. Between the longitudinally opposite outer sides extending collecting chambers 6 and 10, a third collecting space 18 is provided which extends parallel to the outer collecting chambers 6, 10 centrally. This collecting space 18 has the fluid inlet 8, and at each of the outer collecting chambers 6, 10, a fluid outlet 12 is provided. Input 8 and output 12 are located respectively on the same end face, ie the narrow side of the rectangular in cross-section plenums 6, 10, 18. In this arrangement results on each side of the central plenum 18 in the fluid guides 14, the half volume flow through the entrance 8 entering fluid flow. If the run length is halved, the pressure loss is reduced to one quarter of the value set at full run length and full volume flow. As a result, even with thin-walled components which enable a high efficiency of the heat exchange, a heat exchange device can be realized which is characterized by good operating characteristics even at the viscosity ranges given at low temperatures. The central collecting space 18, which is arranged parallel to the outer collecting chambers 6, 10, has the same shape and the same volume as the outer collecting chambers 6, 10. The second exemplary embodiment shown in FIG. 4 corresponds to the example of FIG. 3, except that the outer collecting chambers 6, 10 form the input side, each with a fluid inlet 8, while the central collecting chamber 18 has the fluid outlet 12. During operation, the same conditions with respect to run lengths, volume flows and pressure losses in the fluid guides 14 again arise, as is the case in the example of FIG. 3.

In the embodiments of FIGS. 5, 6 and 7, the entire heat exchange device 2, instead of a single, centrally located between the outer collecting chambers 6 and 10 collecting space 18 has two central plenums 20 and 22. As a result, the entire heat exchange device 2 is divided into two heat exchangers 24 and 26. All collecting chambers 6, 10, 20 and 22 have the same shape as boxes of rectangular cross-section and have the same volume. The two outer collecting chambers 6 and 10 each have a fluid inlet 8 as input sides, and the centrally located collecting chambers 2 and 22 each have a fluid outlet 12. Inputs 8 and outputs 12 are each arranged on the same end face of the collecting spaces 6, 10, 20, 22. For the fluid flow, corresponding flow conditions result as in the two first exemplary embodiments of FIGS. 3 and 4, that is to say the shortened run lengths at half the volume flow in the fluid guides 14 and with the resulting advantages for winter operation.

The embodiment of FIG. 6 corresponds to the embodiment of FIG. 5, except that the central plenums 20 and 22 form the input sides with the inputs 8, while the outer plenums 6 and 10 have the outputs 12. The division of the entire heat exchanger device 2 into the heat exchangers 24 and 26 also makes it possible to adapt to special installation situations by selecting the mutual positional arrangement of the heat exchangers 24 and 26. The embodiment of FIG. 7 corresponds, as regards the arrangement of the collecting chambers 6, 10, 20 and 22, to the examples of FIGS. 5 and 6. In contrast to this, however, only the left side heat exchanger 24 in FIG. 7 has a fluid inlet 8 and a fluid outlet 12. The input 8 having collection space 20 is connected to the input 8 opposite front end via a line 28 to the adjacent end face of the collecting space 22 of the other heat exchanger 26. Furthermore, the two outer collecting chambers 6 and 10 are connected via a line 30, which opens at the output 12 opposite end face of the collecting space 6 in this. In this arrangement, although the embodiment of FIG. 7, like the examples of FIGS. 5 and 6, is composed of two heat exchangers 24, 26, it has only two external connections, namely an input 8 and an output 12. The lines 28, 30 can as pipe or

Be executed hose lines. In all embodiments, pressure-operated Bypassven- tileinrichtungen can be arranged between the input and output sides.

Claims

P a n t a n s p r e c h e

Heat exchange device (2), in particular fluid-air heat exchanger, with individual fluid-carrying collecting chambers (6, 10), each having an input (8) or output (12) for the fluid supply and discharge and via channel-like fluid guides (14 ), which in the operation of the device temper a fluid flow by means of an air flow, in particular cool, which flows in channel-like air ducts which are separated from the fluid guides (14) in a media-tight manner, characterized in that for the construction of the entire heat exchange device (2) between collecting spaces (6, 10), which are arranged on mutually opposite outer sides, at least one further collecting space (18; 20, 22) is inserted, which is arranged in parallel to the outer collecting spaces (6, 10) and in all with a lying outside collecting space (6, 10) connected fluid guides (14) alike.

Heat exchange device according to claim 1, characterized in that a collecting space (18) is located centrally between two via the fluid guides (14) connected to the outside collecting spaces (6, 10) and an input (8) or an output (12) and that the outer collecting chambers (6, 10) have an outlet (12) or an inlet (8).

Heat exchange device according to claim 1 or 2, characterized in that at least two fluid-air heat exchangers (24, 26) are used, which, preferably arranged in a plane, with their adjacent collecting chambers (20, 22) facing in a common fluid flow direction and an output (12) or a Have input (8), and that the channel-like fluid guides (14) each connected collecting chambers (6, 10) form the output (12) or input (8) for the fluid.

4. Heat exchange device according to one of the preceding claims, characterized in that at least two fluid-air-heat exchanger (24, 26), preferably connected in series, are used, of which in each case a collecting space (20, 22) has an inlet (8 ) or output (12) and in a series arrangement via a line (28) to the next collecting space (20, 22) of a further heat exchanger (24, 26) is connected.

5. Heat exchange device according to claim 4, characterized in that in a series arrangement connected to each other collecting spaces (20, 22) have a mutually opposite flow direction during operation of the device (2).

6. Heat exchange device according to claim 5, characterized in that the further collecting space (6, 10) of the one heat exchanger (24, 26) connected in a series arrangement further heat exchanger (24, 26) via a further line (30) to the collecting space ( 6, 10) of the other heat exchanger (6, 10) is connected, which has at its opposite end an output (12).

7. Heat exchange device according to one of the preceding claims, characterized in that the collecting chambers (6, 10, 18, 20, 22) with one (8) or outputs (12) via the channel-like fluid guides (14) only one collecting space (6, 10, 18, 20, 22) with an output (12) or input (8) supply.

8. Heat exchange device according to one of the preceding claims, characterized in that the respectively used collecting spaces (6, 10, 18, 20, 22) are chosen to be equal in volume.

9. Heat exchange device according to one of the preceding claims, characterized in that over the entire height or length of a designed in the manner of a collecting tank collecting space (6, 10, 28, 20, 22), the channel-like fluid guides (14) open into this and that the Air flow during operation of the device substantially transversely to the air ducts (14) in the connected collecting space (6, 10, 18, 20, 22) takes place.

10. Heat exchange device according to one of the preceding claims, characterized in that a fan device is preferably arranged on the front side of the channel-like fluid guides (14) in order for such an efficient heat exchange, in particular cooling, to increase the air flow.