EP1711770B1 - Cooling apparatus, especially for cooling compressed air - Google Patents

Cooling apparatus, especially for cooling compressed air Download PDF

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EP1711770B1
EP1711770B1 EP05700897A EP05700897A EP1711770B1 EP 1711770 B1 EP1711770 B1 EP 1711770B1 EP 05700897 A EP05700897 A EP 05700897A EP 05700897 A EP05700897 A EP 05700897A EP 1711770 B1 EP1711770 B1 EP 1711770B1
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cooling
air
fan
radial
pressure chamber
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EP1711770A1 (en
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Wolfgang Riese
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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
    • F28D1/0233—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 air flow channels
    • F28D1/024—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 air flow channels with an air driving element

Definitions

  • the invention relates to a cooling device according to the preamble of claim 1, which generally serves for cooling a hot flow medium and preferably for cooling the compressed air generated by a compressor US 2003/0047151 describes such a cooling device.
  • the cooling device is provided for use in compressors, in particular screw compressors, which are mounted on silo vehicles and provide compressed air for the pneumatic conveying of a bulk material to be transported in the silo vehicle.
  • the compressed air coolers are usually installed in the immediate vicinity of the compressor stage and inserted into the compressed air system.
  • Compressed air coolers are known in which the radiator body through which the compressed air flows, which has the form of a cooling grid or cooling network, is acted on by an axial fan with cooling air. This is located because of the cramped space in the smallest possible distance from the plane air inlet surface of the cooling grid.
  • the cooling air flow generated by the axial fan is circular and acts essentially only on a circular partial surface of the total square air inlet surface of the cooling grid.
  • the surface areas of the cooling grid which lie outside this circular partial area remain more or less unaffected by the cooling air.
  • the effective efficiency of the cooling grid is thus utilized only to about 60 to 70%. This applies regardless of whether the axial fan is arranged in sucking or pressing assignment to the cooling grid.
  • axial fans Another disadvantage of axial fans is their low power density and low efficiency.
  • the air flow rate of the axial fan is highly dependent on the backpressure, and the curves show that even at the back pressure of 200 Pa, the air flow and thus also the cooling capacity is reduced by about 50%.
  • the cooling capacity was not sufficient to z. B. at an ambient temperature of 30 ° C and a compressed air flow rate of 1,000 m 3 / h, the compressed air to a final temperature of less than 100 ° C to cool.
  • the object of the invention is to improve a cooling device of the specified type so that it is the cramped space conditions of silo vehicles justice and provides optimal cooling performance that is sufficient to a compressed air flow to a temperature in the range of ambient or the intake temperature to cool, without the space required for the cooling device is increased.
  • Another condition is to ensure by controlling or regulating the cooling capacity that a shortfall of the dew point is prevented.
  • the falling below the dew point in the compressed air condensate may indeed in the promotion of certain goods such.
  • B. PVC granules may be advantageous because it prevents the electrostatic charge. In general, especially in absorbent goods such. As flour, gypsum and cement, condensate is undesirable because it leads to sticking and pneumatic delivery can even make impossible.
  • a comparison of the performance parameters of axial fans and centrifugal fans shows that axial valves already have a power loss of 50% at a flow resistance or back pressure of 200 Pa, while in radial blowers such a power loss occurs only at a back pressure of 600 Pa.
  • radial blowers there is the difficulty that their air outlet surface has relatively small dimensions, which in itself unfavorable for the uniform application of a larger cooling surface, such.
  • B. the square air inflow of a cooling grid or cooling network, is.
  • the invention overcomes this difficulty in that a pre-pressure chamber is arranged in front of the heat sink, which has at least one air inlet opening, to which the air outlet of a radial fan is connected.
  • the admission pressure chamber allows that of the radial fan, preferably generated by a plurality of radial fans cooling air flow evenly distributed to the surface of the heat sink. For this purpose, a minimum height of the admission pressure chamber is required.
  • the cooling device shown in the drawings has a heat sink serving as a heat sink 1 of flat cuboid or box shape with a cooling grid or cooling network 3 and an upper and lower manifold chamber 5.
  • a heat sink serving as a heat sink 1 of flat cuboid or box shape with a cooling grid or cooling network 3 and an upper and lower manifold chamber 5.
  • In operation flows from a compressor (not shown) compressed and thereby heated compressed air, z. B. from the upper manifold chamber 5 to the lower manifold chamber 5 by a plurality of provided with cooling fins or cooling fins tubes, which together form the cooling grid 3.
  • the cooling grid 3 is flowed through by a cooling air flow, which is generated by a plurality of radial blowers 7.
  • a cooling air flow which is generated by a plurality of radial blowers 7.
  • six radial blowers 7 are provided, with two radial blowers 7 each have a common, arranged between them drive motor 9 and thus form a radial double fan.
  • Each radial fan 7 has a fan with a rectangular, the cooling grid 3 facing air outlet opening 14th
  • each radial fan 7 which may be of a known and commercially available design, has its own fan housing with a curved peripheral wall 8 circumferentially surrounding the radial fan motor (not shown) and parallel to its axis, and two towards the axis of the radial Blower motor vertical end walls 10, in which the inflow openings 12 of the radial fan are arranged.
  • the enclosed by the peripheral wall 8 and the end walls 10 rectangular air outlet opening 14 ( Fig. 2 ) lies in a plane parallel to the axis of the fan rotor.
  • a pressure chamber 11 which has the shape of a flat, one-sided open box, the open side of the cooling grid 3 is facing.
  • the closed wall of the pressure chamber 11 has a number of rectangular air inlet openings 13, whose size, number and arrangement corresponds to those of the air outlet openings 14 of the individual radial fan 7.
  • the radial fan 7 are mounted on the rear wall of the pressure chamber 11 such that their air outlet openings 14 come to the air inlet openings 13 of the pressure chamber 11 to cover. Subsequently, the pressure chamber 11 is sealingly attached to the heat sink 1. For this purpose, the pressure chamber 11 z. B. flanges 15 with holes for mounting screws.
  • the individual radial fan 7 have in comparison to the surface of the heat sink 1 small dimensions, so that the limited space is taken into account.
  • a plurality of radial fans are evenly distributed over the surface of the pressure chamber 11 and thus evenly over the air inlet surface of the cooling grid 3, the total area of the cooling grid 3 is uniformly acted upon by the cooling air flow.
  • the height h of the pressure chamber 11 (s. Fig.
  • each air inlet opening 13 is dimensioned to be in a predetermined relation to the circumferential length and the area of each of the air inlets 13. This relation is such that the product of the height h and the circumferential length of each air inlet opening 13 is 1 to 3 times, preferably about 2 times, the area of each air inlet opening 13.
  • each air inlet opening 13 has side lengths of 10 or 6 cm and thus an area of 60 cm 2 and a total circumferential length of 32 cm.
  • the height h of the pressure chamber 11 is 4 cm.
  • the product of the height h and the circumferential length of each air inlet opening 13 is thus 128 cm 2 . This product is a measure of the flow area available to the blower air flow entering each air inlet 13 for lateral spread prior to impingement on the chilled grate 13.
  • the double-radial blowers 7 can be controlled or regulated by means of an integrated electronic control unit (not shown) , Via an externally controlled control control device (not shown), in which inter alia an analog-digital temperature display and a control potentiometer is located, can the fan speed or the cooling temperature continuously between 40 ° C and 120 ° C, based on an outside temperature of 20 ° C, adjust or regulate.
  • the invention is not limited to the details of the illustrated embodiment.
  • the number and arrangement of the radial fan 7 can be changed and adapted to the predetermined dimensions of the cooling grid 3, to the predetermined dimensions of the heat sink 1 and to the available space.
  • a protective housing 17 is shown (in Fig. 1 and Fig. 3 omitted), which at least partially consists of perforated plate and through which the sucked by the radial fans 7 cooling air can flow.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

Disclosed is an apparatus for cooling a hot flowing medium, particularly compressed air discharged from a compressor. Said cooling apparatus comprises a cooling member in the form of a cooler grid which is penetrated by the medium that is to be cooled, said cooling member acting as a heat exchanger, and a fan system for directing a flow of cooling air onto a substantially flat cooling air inlet area of the cooling member. According to the invention, the fan system encompasses at least one, preferably several radial fans while a preliminary pressure chamber is disposed upstream of the cooling air inlet area of the cooling member, said preliminary pressure chamber being provided with at least one air intake port to which the air outlet of one respective radial fan is connected.

Description

Die Erfindung betrifft eine Kühlvorrichtung gemäß dem Oberbegriff des Anspruchs 1, die allgemein zum Kühlen eines heißen Strömungsmediums und vorzugsweise zum Kühlen der von einem Kompressor erzeugten Druckluft dient US 2003/0047151 beschreibt eine derartige Kühlvorrichtung. Vorzugsweise ist die Kühlvorrichtung vorgesehen zur Verwendung bei Kompressoren, insbesondere Schraubenkompressoren, die an Silo-Fahrzeugen montiert sind und Druckluft zur pneumatischen Förderung eines im Silo-Fahrzeug zu transportierenden Schüttgutes liefern.The invention relates to a cooling device according to the preamble of claim 1, which generally serves for cooling a hot flow medium and preferably for cooling the compressed air generated by a compressor US 2003/0047151 describes such a cooling device. Preferably, the cooling device is provided for use in compressors, in particular screw compressors, which are mounted on silo vehicles and provide compressed air for the pneumatic conveying of a bulk material to be transported in the silo vehicle.

Wegen der stark eingeschränkten Platzverhältnisse an Silo-Fahrzeugen werden die Druckluftkühler in der Regel in unmittelbarer Nähe der Kompressorstufe installiert und in das Druckluftsystem eingefügt. Bekannt sind Druckluftkühler, bei denen der von der Druckluft durchströmte Kühlerkörper, der die Form eines Kühlgitters oder Kühlnetzes hat, durch einen Axialventilator mit Kühlluft beaufschlagt wird. Dieser ist wegen der beengten Platzverhältnisse in kleinstmöglichem Abstand von der ebenen Lufteintrittsfläche des Kühlgitters angeordnet. Der vom Axialventilator erzeugte Kühlluftstrom ist kreisförmig und beaufschlagt im wesentlichen nur eine kreisförmige Teilfläche der insgesamt quadratischen Lufteintrittsfläche des Kühlgitters. Die außerhalb dieser kreisförmigen Teilfläche liegenden Flächenbereiche des Kühlgitters bleiben mehr oder weniger von der Kühlluft unbeaufschlagt. Der effektive Wirkungsgrad des Kühlgitters wird somit nur zu ca. 60 bis 70 % ausgenutzt. Dies gilt unabhängig davon, ob der Axialventilator in saugender oder drückender Zuordnung zum Kühlgitter angeordnet ist.Because of the very limited space available on silo vehicles, the compressed air coolers are usually installed in the immediate vicinity of the compressor stage and inserted into the compressed air system. Compressed air coolers are known in which the radiator body through which the compressed air flows, which has the form of a cooling grid or cooling network, is acted on by an axial fan with cooling air. This is located because of the cramped space in the smallest possible distance from the plane air inlet surface of the cooling grid. The cooling air flow generated by the axial fan is circular and acts essentially only on a circular partial surface of the total square air inlet surface of the cooling grid. The surface areas of the cooling grid which lie outside this circular partial area remain more or less unaffected by the cooling air. The effective efficiency of the cooling grid is thus utilized only to about 60 to 70%. This applies regardless of whether the axial fan is arranged in sucking or pressing assignment to the cooling grid.

Ein weiterer Nachteil von Axialventilatoren ist deren geringe Leistungsdichte bzw. niedriger Wirkungsgrad. Die Luftfördermenge des Axialventilators ist stark vom Gegendruck abhängig, und die Kennlinien zeigen, dass schon bei dem Gegendruck von 200 Pa die Luftfördermenge und damit auch die Kühlleistung sich um ca. 50 % verringert. Bei den bisherigen Systemen war die Kühlleistung nicht ausreichend, um z. B. bei einer Umgebungstemperatur von 30°C und einem Druckluft-Volumenstrom von 1.000 m3/h die Druckluft auf eine Endtemperatur von weniger als 100°C zu kühlen.Another disadvantage of axial fans is their low power density and low efficiency. The air flow rate of the axial fan is highly dependent on the backpressure, and the curves show that even at the back pressure of 200 Pa, the air flow and thus also the cooling capacity is reduced by about 50%. In the previous systems, the cooling capacity was not sufficient to z. B. at an ambient temperature of 30 ° C and a compressed air flow rate of 1,000 m 3 / h, the compressed air to a final temperature of less than 100 ° C to cool.

Aufgabe der Erfindung ist es, eine Kühlvorrichtung der angegebenen Art so zu verbessern, dass sie den beengten Platzverhältnissen an Silo-Fahrzeugen gerecht wird und eine optimale Kühlleistung bietet, die ausreicht, um einen Druckluftstrom auf eine Temperatur im Bereich der Umgebungs- bzw. der Ansaugtemperatur zu kühlen, ohne dass der Platzbedarf für die Kühlvorrichtung vergrößert wird.The object of the invention is to improve a cooling device of the specified type so that it is the cramped space conditions of silo vehicles justice and provides optimal cooling performance that is sufficient to a compressed air flow to a temperature in the range of ambient or the intake temperature to cool, without the space required for the cooling device is increased.

Eine weitere Bedingung besteht darin, durch Steuerung oder Regelung der Kühlleistung sicherzustellen, dass eine Unterschreitung des Taupunktes verhindert wird. Das bei Unterschreitung des Taupunktes in der Druckluft anfallende Kondensat kann zwar bei der Förderung bestimmter Güter wie z. B. PVC-Granulat vorteilhaft sein, da es die elektrostatische Aufladung verhindert. In der Regel, insbesondere bei saugfähigen Fördergütern wie z. B. Mehl, Gips und Zement, ist Kondensat aber unerwünscht, da es zu Verklebungen führt und eine pneumatische Förderung sogar unmöglich machen kann.Another condition is to ensure by controlling or regulating the cooling capacity that a shortfall of the dew point is prevented. The falling below the dew point in the compressed air condensate may indeed in the promotion of certain goods such. B. PVC granules may be advantageous because it prevents the electrostatic charge. In general, especially in absorbent goods such. As flour, gypsum and cement, condensate is undesirable because it leads to sticking and pneumatic delivery can even make impossible.

Die erfindungsgemäße Lösung der Aufgabe ist im Anspruch 1 angegeben. Die Unteransprüche beziehen sich auf weitere vorteilhafte Ausgestaltungen der Erfindung.The achievement of the object according to the invention is specified in claim 1. The subclaims relate to further advantageous embodiments of the invention.

Ein Vergleich der Leistungsparameter von Axialventilatoren und Radialgebläsen zeigt, dass Axialventialtoren bereits bei einem Strömungswiderstand bzw. Gegendruck von 200 Pa einen Leistungsverlust von 50 % aufweisen, während bei Radialgebläsen ein solcher Leistungsverlust erst bei einem Gegendruck bzw. Strömungswiderstand von 600 Pa eintritt. Bei Radialgebläsen besteht jedoch die Schwierigkeit, dass ihre Luftaustrittsfläche relativ kleine Abmessungen aufweist, die an sich ungünstig für die gleichmäßige Beaufschlagung einer größeren Kühlfläche, wie z. B. der quadratischen Lufteinströmfläche eines Kühlgitters oder Kühlnetzes, ist. Die Erfindung überwindet diese Schwierigkeit dadurch, dass vor dem Kühlkörper eine Vordruckkammer angeordnet wird, die mindestens eine Lufteintrittsöffnung aufweist, an die der Luftauslass eines Radialgebläses angeschlossen ist. Die Vordruckkammer ermöglicht es, dass sich der von dem Radialgebläse, vorzugsweise von einer Mehrzahl von Radialgebläsen erzeugte Kühlluftstrom gleichmäßig auf die Fläche des Kühlkörpers verteilt. Hierzu ist eine Mindesthöhe der Vordruckkammer erforderlich.A comparison of the performance parameters of axial fans and centrifugal fans shows that axial valves already have a power loss of 50% at a flow resistance or back pressure of 200 Pa, while in radial blowers such a power loss occurs only at a back pressure of 600 Pa. In radial blowers, however, there is the difficulty that their air outlet surface has relatively small dimensions, which in itself unfavorable for the uniform application of a larger cooling surface, such. B. the square air inflow of a cooling grid or cooling network, is. The invention overcomes this difficulty in that a pre-pressure chamber is arranged in front of the heat sink, which has at least one air inlet opening, to which the air outlet of a radial fan is connected. The admission pressure chamber allows that of the radial fan, preferably generated by a plurality of radial fans cooling air flow evenly distributed to the surface of the heat sink. For this purpose, a minimum height of the admission pressure chamber is required.

Eine Ausführungsform der Erfindung wird anhand der Zeichnungen näher erläutert. Es zeigt:

Fig. 1
eine perspektivische Ansicht der Kühlvorrichtung,
Fig. 2
in etwas größerem Maßstab einen Schnitt durch die Kühlvorrichtung etwa entlang ihrer vertikalen Mittelebene,
Fig. 3
eine perspektivische Darstellung der Hauptkomponenten der Kühlvorrich- tung vor dem Zusammenbau.
An embodiment of the invention will be explained in more detail with reference to the drawings. It shows:
Fig. 1
a perspective view of the cooling device,
Fig. 2
on a somewhat larger scale a section through the cooling device approximately along its vertical center plane,
Fig. 3
a perspective view of the main components of the Kühlvorrich- device before assembly.

Die in den Zeichnungen dargestellte Kühlvorrichtung hat einen als Wärmetauscher dienenden Kühlkörper 1 von flacher Quader- bzw. Kastenform mit einem Kühlgitter oder Kühlnetz 3 sowie einer oberen und unteren Verteilerkammer 5. Im Betrieb strömt von einem Kompressor (nicht dargestellt) verdichtete und dabei erwärmte Druckluft, z. B. aus der oberen Verteilerkammer 5 zur unteren Verteilerkammer 5 durch eine Vielzahl von mit Kühlrippen oder Kühllamellen versehene Röhren, die zusammen das Kühlgitter 3 bilden.The cooling device shown in the drawings has a heat sink serving as a heat sink 1 of flat cuboid or box shape with a cooling grid or cooling network 3 and an upper and lower manifold chamber 5. In operation flows from a compressor (not shown) compressed and thereby heated compressed air, z. B. from the upper manifold chamber 5 to the lower manifold chamber 5 by a plurality of provided with cooling fins or cooling fins tubes, which together form the cooling grid 3.

In den Zwischenräumen zwischen den Kühlrippen oder -lamellen wird das Kühlgitter 3 durchströmt von einem Kühlluftstrom, der von einer Mehrzahl von Radialgebläsen 7 erzeugt wird. Bei dem Ausführungsbeispiel sind sechs Radialgebläse 7 vorgesehen, wobei jeweils zwei Radialgebläse 7 einen gemeinsamen, zwischen ihnen angeordneten Antriebsmotor 9 aufweisen und somit ein Radial-Doppelgebläse bilden. Jedes Radialgebläse 7 hat ein Gebläse mit einer rechteckigen, dem Kühlgitter 3 zugewandten Luftaustrittsöffnung 14.In the spaces between the cooling ribs or fins, the cooling grid 3 is flowed through by a cooling air flow, which is generated by a plurality of radial blowers 7. In the embodiment, six radial blowers 7 are provided, with two radial blowers 7 each have a common, arranged between them drive motor 9 and thus form a radial double fan. Each radial fan 7 has a fan with a rectangular, the cooling grid 3 facing air outlet opening 14th

Genauer gesagt hat jedes Radialgebläse 7, das von bekannter und im Handel erhältlicher Bauart sein kann, ein eigenes Gebläsegehäuse mit einer gekrümmten, den Radial-Gebläserotor (nicht dargestellt) mit Abstand umgebenden und zu dessen Achse parallelen Umfangswand 8, und zwei zur Achse des Radial-Gebläserotors senkrechten Stirnwänden 10, in denen die Einströmöffnungen 12 des Radialgebläses angeordnet sind. Die von der Umfangswand 8 und den Stirnwänden 10 umgrenzte rechteckige Luftaustrittsöffnung 14 (Fig. 2) liegt in einer zur Achse des Gebläserotors parallelen Ebene.More specifically, each radial fan 7, which may be of a known and commercially available design, has its own fan housing with a curved peripheral wall 8 circumferentially surrounding the radial fan motor (not shown) and parallel to its axis, and two towards the axis of the radial Blower motor vertical end walls 10, in which the inflow openings 12 of the radial fan are arranged. The enclosed by the peripheral wall 8 and the end walls 10 rectangular air outlet opening 14 ( Fig. 2 ) lies in a plane parallel to the axis of the fan rotor.

Zwischen dem Kühlgitter 3 und den Radialgebläsen 7 befindet sich eine Druckkammer 11, die die Form eines flachen, einseitig offenen Kastens hat, dessen offene Seite dem Kühlgitter 3 zugewendet ist. Die geschlossene Wandung der Druckkammer 11 weist eine Anzahl von rechteckigen Lufteintrittsöffnungen 13 auf, deren Größe, Anzahl und Anordnung diejenigen der Luftaustrittsöffnungen 14 der einzelnen Radialgebläse 7 entspricht.Between the cooling grid 3 and the radial fans 7 is a pressure chamber 11, which has the shape of a flat, one-sided open box, the open side of the cooling grid 3 is facing. The closed wall of the pressure chamber 11 has a number of rectangular air inlet openings 13, whose size, number and arrangement corresponds to those of the air outlet openings 14 of the individual radial fan 7.

Für den Zusammenbau der Kühlvorrichtung werden die Radialgebläse 7 auf der Rückwand der Druckkammer 11 derart montiert, dass ihre Luftaustrittsöffnungen 14 mit den Lufteintrittsöffnungen 13 der Druckkammer 11 zur Deckung kommen. Anschließend wird die Druckkammer 11 abdichtend an dem Kühlkörper 1 befestigt. Zu diesem Zweck kann die Druckkammer 11 z. B. Flansche 15 mit Löchern für Befestigungsschrauben aufweisen.For the assembly of the cooling device, the radial fan 7 are mounted on the rear wall of the pressure chamber 11 such that their air outlet openings 14 come to the air inlet openings 13 of the pressure chamber 11 to cover. Subsequently, the pressure chamber 11 is sealingly attached to the heat sink 1. For this purpose, the pressure chamber 11 z. B. flanges 15 with holes for mounting screws.

Die einzelnen Radialgebläse 7 haben im Vergleich zur Fläche des Kühlkörpers 1 kleine Abmessungen, so dass den beengten Platzverhältnissen Rechnung getragen wird. Da jedoch mehrere Radialgebläse gleichmäßig über die Fläche der Druckkammer 11 und damit auch gleichmäßig über die Lufteintrittsfläche des Kühlgitters 3 verteilt sind, wird die Gesamtfläche des Kühlgitters 3 gleichmäßig von dem Kühlluftstrom beaufschlagt wird. Dabei muss jedoch sichergestellt werden, dass der aus jeder Lufteintrittsöffnung 13 in die Druckkammer 11 eintretende Luftstrom sich auch seitlich ohne übermäßigen Strömungswiderstand ausbreiten kann, um die Lufteintrittsfläche des Kühlgitters 3 gleichmäßig, auch außerhalb der Kontur jeder Lufteintrittsöffnung 13, zu beaufschlagen. Um dies zu gewährleisten, ist erfindungsgemäß die Höhe h der Druckkammer 11 (s. Fig. 2) so bemessen, dass sie in einer vorgegebenen Relation zu der Umfangslänge und der Fläche jeder der Lufteintrittsöffnungen 13 steht. Diese Relation ist derart, dass das Produkt aus der Höhe h und der Umfangslänge jeder Lufteintrittsöffnung 13 das 1- bis 3-fache, vorzugsweise ca. das 2-fache, der Fläche jeder Lufteintrittsöffnung 13 beträgt.The individual radial fan 7 have in comparison to the surface of the heat sink 1 small dimensions, so that the limited space is taken into account. However, since a plurality of radial fans are evenly distributed over the surface of the pressure chamber 11 and thus evenly over the air inlet surface of the cooling grid 3, the total area of the cooling grid 3 is uniformly acted upon by the cooling air flow. However, it must be ensured that the air flow entering from each air inlet opening 13 into the pressure chamber 11 can also propagate laterally without excessive flow resistance, around the air inlet surface of the cooling grid 3 evenly, even outside the contour of each air inlet opening 13 apply. To ensure this, according to the invention, the height h of the pressure chamber 11 (s. Fig. 2 ) is dimensioned to be in a predetermined relation to the circumferential length and the area of each of the air inlets 13. This relation is such that the product of the height h and the circumferential length of each air inlet opening 13 is 1 to 3 times, preferably about 2 times, the area of each air inlet opening 13.

Bei einem konkreten Ausführungsbeispiel hat jede Lufteintrittsöffnung 13 Seitenlängen von 10 bzw. 6 cm und somit eine Fläche von 60 cm2 und eine gesamte Umfangslänge von 32 cm. Die Höhe h der Druckkammer 11 beträgt 4 cm. Das Produkt aus der Höhe h und der Umfangslänge jeder Lufteintrittsöffnung 13 beträgt somit 128 cm2. Dieses Produkt ist ein Maß für den Strömungsquerschnitt, der dem durch jede Lufteintrittsöffnung 13 eintretenden Gebläseluftstrom für die seitliche Ausbreitung vor dem Auftreffen auf das Kühlgitter 13 zur Verfügung steht.In a specific embodiment, each air inlet opening 13 has side lengths of 10 or 6 cm and thus an area of 60 cm 2 and a total circumferential length of 32 cm. The height h of the pressure chamber 11 is 4 cm. The product of the height h and the circumferential length of each air inlet opening 13 is thus 128 cm 2 . This product is a measure of the flow area available to the blower air flow entering each air inlet 13 for lateral spread prior to impingement on the chilled grate 13.

Es hat sich gezeigt, dass bei einer erfindungsgemäßen Kühlvorrichtung, bei der der bisher verwendete Axialventilator durch die dargestellte Anordnung von Radialgebläsen 7 mit Druckkammer 11 ersetzt wurde, die Austrittstemperatur der Druckluft aus der Kühlvorrichtung von bisher 100°C auf 50°C gesenkt werden konnte. Dies liegt daran, dass die von den Doppel-Radialgebläsen 7, aufgrund der zur Verfügung stehenden höheren Leistungsdichte, mit erhöhtem Druck in die Druckkammer 11 eingebrachte Luftmenge das Kühlgitter 3 flächendeckend beaufschlagt und mit maximaler Strömungsgeschwindigkeit gleichmäßig durchströmt.It has been shown that in a cooling device according to the invention, in which the previously used axial fan was replaced by the illustrated arrangement of radial blowers 7 with pressure chamber 11, the outlet temperature of the compressed air from the cooling device of previously 100 ° C to 50 ° C could be lowered. This is due to the fact that the amount of air introduced by the double radial fans 7, due to the higher power density available, into the pressure chamber 11 with increased pressure acts on the cooling grid 3 across the surface and flows through it evenly with maximum flow velocity.

Um dem Betreiber die Möglichkeit zu bieten, die für das jeweilige Fördergut erforderliche Kühlleistung einzustellen und ggf. eine durch zu starke Kühlung verursachte Unterschreitung des Taupunktes zu vermeiden, sind die Doppel-Radialgebläse 7 mittels einer integrierten elektronischen Steuereinheit (nicht dargestellt) steuerbar bzw. regelbar. Über ein extern gesteuertes Steuerkontrollgerät (nicht dargestellt), in dem sich unter anderem eine analog-digitale Temperaturanzeige sowie ein Regel-Potentiometer befindet, läßt sich die Gebläseleistung bzw. die Kühltemperatur stufenlos zwischen 40°C und 120°C, bezogen auf eine Außentemperatur von 20°C, einstellen bzw. regeln.In order to offer the operator the opportunity to adjust the cooling capacity required for the respective conveyed material and, if necessary, to prevent the dew point from being undershot caused by excessive cooling, the double-radial blowers 7 can be controlled or regulated by means of an integrated electronic control unit (not shown) , Via an externally controlled control control device (not shown), in which inter alia an analog-digital temperature display and a control potentiometer is located, can the fan speed or the cooling temperature continuously between 40 ° C and 120 ° C, based on an outside temperature of 20 ° C, adjust or regulate.

Die Erfindung ist nicht auf die Einzelheiten der dargestellten Ausführungsform beschränkt. So kann insbesondere die Anzahl und Anordnung der Radialgebläse 7 geändert und an die vorgegebenen Abmessungen des Kühlgitters 3, an die vorgegebenen Abmessungen des Kühlkörpers 1 und an die vorhandenen Platzverhältnisse anpassen.The invention is not limited to the details of the illustrated embodiment. Thus, in particular, the number and arrangement of the radial fan 7 can be changed and adapted to the predetermined dimensions of the cooling grid 3, to the predetermined dimensions of the heat sink 1 and to the available space.

In Fig. 2 ist ein Schutzgehäuse 17 dargestellt (in Fig. 1 und Fig. 3 weggelassen), welches mindestens teilweise aus Lochblech besteht und durch welches die von den Radialgebläsen 7 angesaugte Kühlluft einströmen kann.In Fig. 2 a protective housing 17 is shown (in Fig. 1 and Fig. 3 omitted), which at least partially consists of perforated plate and through which the sucked by the radial fans 7 cooling air can flow.

Claims (7)

  1. A cooling apparatus for cooling a hot fluid medium, in particular compressed air emerging from a compressor,
    with a cooling body (1) serving as a heat exchanger and in the form of a radiator grille (radiator block) (3) through which the medium to be cooled flows, and with a fan assembly for directing a cooling air flow on to a substantially flat cooling-air inlet area of the cooling body, characterised in that upstream of the cooling-air inlet area of the cooling body (1) a pressure chamber (11) is disposed which has at least one air-inlet opening (13), to which the air outlet of a radial fan (7) is connected.
  2. An apparatus according to Claim 1, characterised in that a plurality of air-inlet openings (13), preferably uniformly spaced apart, are arranged in the wall of the pressure chamber (11), a radial fan (7) being connected to each of the air-inlet openings.
  3. An apparatus according to Claim 1 or 2, characterised in that in each case two radial fans (7) are combined to form one radial double fan with a common drive motor (9).
  4. An apparatus according to any one of Claims 1 to 3, characterised in that the wall of the pressure chamber (11) provided with the air-inlet openings extends substantially parallel to the air-inlet area of the cooling body (1) at a distance (h) therefrom which is of such dimensions that the product of the distance (h) and the peripheral length of each air-inlet opening (13) is equal to or greater than the area of each air-inlet opening.
  5. An apparatus according to Claim 4, characterised in that the product is equal to 1 to 3 times, preferably equal to 2 times, the area of each air-inlet opening (13).
  6. An apparatus according to any one of Claims 1 to 5, characterised in that it has a device for varying or controlling the speed of rotation of each radial fan (7).
  7. An apparatus according to any one of Claims 1 to 6, characterised in that the or each radial fan (7) has a fan housing with a curved circumferential wall (8) parallel to the axis of the fan rotor and two end walls (10) which are perpendicular to the axis of the fan rotor and which define a rectangular air-outlet opening (14) of the radial fan.
EP05700897A 2004-01-19 2005-01-13 Cooling apparatus, especially for cooling compressed air Active EP1711770B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202004000733U DE202004000733U1 (en) 2004-01-19 2004-01-19 Cooling device, in particular for cooling compressed air
PCT/EP2005/000289 WO2005068925A1 (en) 2004-01-19 2005-01-13 Cooling apparatus, especially for cooling compressed air

Publications (2)

Publication Number Publication Date
EP1711770A1 EP1711770A1 (en) 2006-10-18
EP1711770B1 true EP1711770B1 (en) 2010-11-17

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EP05700897A Active EP1711770B1 (en) 2004-01-19 2005-01-13 Cooling apparatus, especially for cooling compressed air

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EP (1) EP1711770B1 (en)
AT (1) ATE488741T1 (en)
DE (2) DE202004000733U1 (en)
WO (1) WO2005068925A1 (en)

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Publication number Priority date Publication date Assignee Title
US6255059B1 (en) 1993-03-31 2001-07-03 Cadus Pharmaceutical Corporation Methods for identifying G protein coupled receptor effectors

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5709175A (en) * 1995-12-19 1998-01-20 Caterpillar Inc. Cooling air system for an engine
EP0840073B1 (en) * 1996-11-01 2003-07-23 Martin Frei Warm-air heating apparatus
DE19713712C1 (en) * 1997-04-03 1998-04-16 Laengerer & Reich Gmbh & Co Radial ventilator for cooling system of motor vehicles
DE19950755A1 (en) * 1999-10-21 2001-04-26 Modine Mfg Co Cooling system III
DE10018089A1 (en) * 2000-04-12 2001-11-29 Modine Mfg Co Box-shaped cooling system for motor vehicles
DE10119591A1 (en) * 2001-04-21 2002-10-24 Modine Mfg Co Cooling system for motor vehicles
DE10120483A1 (en) * 2001-04-25 2002-10-31 Modine Mfg Co Arrangement for cooling
EP1284343B1 (en) * 2001-08-17 2008-07-30 Behr GmbH & Co. KG Cooling system for a motor vehicle and related motor vehicle

Also Published As

Publication number Publication date
EP1711770A1 (en) 2006-10-18
WO2005068925A1 (en) 2005-07-28
DE202004000733U1 (en) 2005-06-09
ATE488741T1 (en) 2010-12-15
DE502005010550D1 (en) 2010-12-30

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