EP3404268A1 - Ventilation unit for refrigeration systems - Google Patents
Ventilation unit for refrigeration systems Download PDFInfo
- Publication number
- EP3404268A1 EP3404268A1 EP18172026.9A EP18172026A EP3404268A1 EP 3404268 A1 EP3404268 A1 EP 3404268A1 EP 18172026 A EP18172026 A EP 18172026A EP 3404268 A1 EP3404268 A1 EP 3404268A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fan
- ventilation unit
- heat exchanger
- designed
- diagonal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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- 238000009423 ventilation Methods 0.000 title claims abstract description 44
- 238000005057 refrigeration Methods 0.000 title claims abstract description 9
- 230000000750 progressive effect Effects 0.000 claims description 3
- 230000003068 static effect Effects 0.000 claims description 2
- 230000000630 rising effect Effects 0.000 claims 1
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 230000001681 protective effect Effects 0.000 description 3
- 238000007664 blowing Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000010257 thawing Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
- F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
- F25D17/067—Evaporator fan units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/06—Helico-centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0025—Cross-flow or tangential fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
- F24F11/43—Defrosting; Preventing freezing of indoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
- F25D2317/0681—Details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2500/00—Problems to be solved
- F25D2500/02—Geometry problems
Definitions
- the invention relates to a ventilation unit designed for use and for arrangement on a refrigeration system.
- the necessary defrosting is generally a disadvantageous, expensive and as far as possible avoidable disturbance process of the actual operation.
- the invention is therefore based on the object to provide a ventilation unit, which overcomes the above disadvantages and can be operated more efficiently and with a lower defrost frequency.
- a ventilation unit is designed for use and for arrangement on a refrigeration system, with a fan and a fan arranged in series in the heat exchanger, wherein the fan is formed and arranged opposite the heat exchanger, during operation, an air flow through the heat exchanger and out of the To promote ventilation unit out.
- the fan is inventively designed as a diagonal fan. In the diagonal fan, the air volume flow is sucked axially during operation and blown diagonally at an angle relative to the axis of rotation of the diagonal fan.
- the diagonal fan is characterized in an advantageous manner by a high air flow even at higher back pressure. In this case, it is ensured that even with the counter pressures occurring maximally in the operation, the discharge direction of the diagonal fan is always diagonal and not radial. Its throwing distance remains essentially unchanged, even in the case of a continuously increasing heat exchanger, and a thermal short circuit through an outward return flow to the intake area of the heat exchanger is prevented. In addition, a resulting greater icing of the heat exchanger is avoided. The defrost cycles of the heat exchanger are extended.
- the diagonal fan is designed to suck the air flow axially and diagonally at an angle of 10 - 80 °, more preferably an angle of 25 - 60 °, to blow out from its axis of rotation.
- the discharge angle of the diagonal fan a priori provides an average value which can be maintained over the operation.
- a favorable embodiment of the ventilation unit provides that the diagonal fan is designed and arranged in the ventilation unit, to suck in the air volume flow through the heat exchanger and to blow it out of the ventilation unit into a free environment, for example in a cold room.
- the diagonal fan is therefore fluidly downstream of the heat exchanger.
- the heat exchanger generates in operation by progressive icing for the diagonal fan from a Popeströmungswiderstand having a first resistance characteristic (A) to an icing resistance with a second resistance characteristic (B) increasing flow resistance.
- the diagonal fan is designed such that its highest efficiency range is in a range of a third resistance characteristic (C) of the heat exchanger, the third resistance characteristic lying between the first and the second resistance characteristic (A, B) ,
- the resistance characteristic curves (A, B, C) are characterized by a backpressure psf [Pa] increasing over a conveyed air volume qv [m 3 / h].
- the outflow remains always diagonal even at maximum back pressures and does not change in a radial direction, such as axial fans.
- the heat exchanger is designed, the air volume flow to cool to a conveyor temperature of less than or equal to 15 ° C, in particular 5 ° C to form a cold air flow rate, the cold air flow is directly sucked and blown by the diagonal fan. Between the heat exchanger and the diagonal fan no cold air volume flow thermally influencing components are provided, the suction through the diagonal fan is directly downstream of the heat exchanger.
- the ventilation unit is characterized in that the diagonal fan and the heat exchanger are connected to one another by a housing, wherein the housing forms a closed flow channel for the air volume flow or the cold air volume flow.
- the ventilation unit is designed as an integral unit for the holistic arrangement and attachment to the refrigeration system.
- the integral assembly can be pre-assembled and delivered as a whole. At the cold rooms only the electrical connection has to be done. The error probability during assembly is thereby reduced.
- the heat exchanger is designed as an evaporator.
- the ventilation unit further comprises a (flow) guide device, which is arranged in a blow-out section of the diagonal fan and designed to deflect the volume of air blown from the diagonal fan in the diagonal direction in an axial direction.
- the diagonal discharge direction of the diagonal fan can thereby be deflected in an axial Ausblasströmungsraum and thus the throw of the diagonal fan can be increased.
- the guide device can be realized by parts of the housing or by additionally attachable to the diagonal fan guide body such as baffles or the like.
- the guide is integrally formed on the diagonal fan, so that the number of parts is minimized.
- Ausblas well can be arranged on the diagonal fan in addition a protective grid or intervention protection.
- the guide partially converts the swirl of the air volume flow generated by the diagonal fan into static pressure and thereby increases the pressure increase, efficiency and throw of the diagonal fan.
- the diagonal fan is formed in a variant with a co-rotating, the fan blades covering the cover plate.
- the ventilation unit can furthermore be designed in such a way that the flow guidance takes place in the stationary housing and the diagonal fan has an axial fan-like wing end. Between the impeller and the fan blades then a gap is provided.
- FIG. 1 The basic structure of the ventilation unit according to the invention is shown schematically, but to illustrate the fluidic problem with an axial fan 11 following a heat exchanger 10. Shown is an icy state of the heat exchanger 10 and a resulting substantially radial outflow of the axial fan 11. About the with Arrows shown flow path 8, it comes to the thermal short circuit, in the blown air of the axial fan 11 back to the intake of the heat exchanger. In addition, there is a discharge-side inflow 9 in the hub region of the axial fan 11, which is superimposed by the outflow. From the actual, provided in the unvereisten state purely axial outflow, as exemplified in FIG. 2 is shown in the iced state of the heat exchanger, nothing or hardly anything left.
- FIG. 3 schematically a ventilation unit 1 according to the invention in the icy state with a diagonal fan 2 and a arranged in series and designed as an evaporator heat exchanger 3 is shown.
- the heat exchanger 3 and the diagonal fan are connected to each other via a flow channel forming housing 5. Both the diagonal fan 2 and the heat exchanger 3 are inserted and fixed in the housing 5, so that the ventilation unit is an integral structural unit.
- a protective grid 19 is arranged at the blow-out portion of the diagonal fan 2.
- the ventilation unit 1 is designed in its schematically illustrated form for use and for arrangement on a refrigeration system.
- the diagonal discharge path 7 is marked with arrows.
- the heat exchanger 3 cools the air volume flow to a conveyor temperature of less than or equal to 15 ° C, in particular less than or equal to 5 ° C, to form the cold air volume flow, which is sucked directly from the diagonal fan 2.
- FIG. 3 with the diagonal fan 2 is opposite to in FIG. 1 shown embodiment with an axial fan 10 in a manner interpretable, as in FIG. 4 is shown on the basis of a graph of the amount of air delivered qv [m 3 / h] against the pressure psf [Pa].
- the fan characteristics 11 ', 2' of the axial fan 11 are made FIG. 1 and the diagonal fan 2 off FIG. 3 and three due to different conditions of icing of the heat exchanger 3 resulting resistance characteristics A, B, C located.
- the flow resistance of the heat exchanger 3 increases in operation by progressive icing of an output flow resistance with a first resistance characteristic A for the diagonal fan to a glacial resistance with a second resistance curve B. In the state of the second resistance characteristic, a defrosting process of the heat exchanger 3 is initiated.
- the diagonal blower 2 is designed, by its diagonal blow-off direction, to have its highest efficiency range in a region of the third resistance characteristic C of the heat exchanger 3, the third resistance characteristic C lying between the first and second resistance characteristics A, B.
- the resistance characteristics A, B, C are characterized by a backpressure psf [Pa] which increases over a conveyed air volume qv [m 3 / h].
- the ventilation unit 1 according to the invention with the diagonal fan 2 can be operated over a longer period of time and with higher efficiency in the region of the resistance characteristic C with a correspondingly large flow rate in comparison with a construction with the axial fan 11, which works only in the area of the resistance characteristic A.
- the absolute difference is characterized by the fan characteristics 11 ', 2' of the axial fan 11 and diagonal fan 2 in the diagram.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Other Air-Conditioning Systems (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
Abstract
Die Erfindung betrifft eine Ventilationseinheit (1) ausgebildet zum Einsatz und zur Anordnung an einer Kälteanlage, mit einem Lüfter und einem zu dem Lüfter in Reihe angeordneten Wärmeübertrager (3), wobei der Lüfter ausgebildet und gegenüber dem Wärmeübertrager (3) angeordnet ist, im Betrieb einen Luftvolumenstrom durch den Wärmeübertrager (3) hindurch und aus der Ventilationseinheit heraus zu fördern, dadurch gekennzeichnet, dass der Lüfter als Diagonallüfter (2) ausgebildet ist und den Luftvolumenstrom im Betrieb axial ansaugt und diagonal in einem Winkel gegenüber seiner Rotationsachse (RA) ausbläst. The invention relates to a ventilation unit (1) designed for use and for arrangement on a refrigeration system, with a fan and a heat exchanger (3) arranged in series with the fan, the fan being designed and arranged opposite the heat exchanger (3) during operation to convey an air volume flow through the heat exchanger (3) and out of the ventilation unit, characterized in that the fan is designed as a diagonal fan (2) and axially draws in the air volume flow during operation and blows diagonally at an angle relative to its axis of rotation (RA).
Description
Die Erfindung betrifft eine Ventilationseinheit ausgebildet zum Einsatz und zur Anordnung an einer Kälteanlage.The invention relates to a ventilation unit designed for use and for arrangement on a refrigeration system.
Beim Einsatz von Ventilationseinheiten mit Lüfter und Wärmeübertagern, die häufig auch als Wärmetauscher bezeichnet werden, an Kälteanlagen ist problematisch, dass der Wärmeübertrager während des Betriebs kontinuierlich zunehmend vereist und mithin sein Strömungswiderstand zunimmt. Der nachgeschaltete Lüfter muss gegen den zunehmenden Strömungswiderstand arbeiten, wodurch sich sein Betriebszustand verändert. Herkömmlicherweise werden bei derartigen Ventilationseinheiten Axiallüfter bzw. Axialventilatoren eingesetzt, die auf den Strömungswiderstand des Wärmetauschers ohne Vereisung ausgelegt werden. Daraus resultiert, dass der Lüfter nur kurzzeitig im Bereich optimaler Effizienz betrieben wird, jedoch mit zunehmender Vereisung des Wärmeübertragers und dessen steigendem Strömungswiderstand sich der Betriebszustand des Lüfters aus dem Bereich des Wirkungsgradoptimums heraus bewegt. Aufgrund des erhöhten Strömungswiderstands verändert sich zudem die Abströmrichtung von einer axialen in eine mehr und mehr radiale Richtung.When using ventilation units with fans and heat exchangers, which are often referred to as heat exchangers, to refrigeration systems is problematic that the heat exchanger during operation continuously increasingly iced and thus increases its flow resistance. The downstream fan must be against the increasing flow resistance work, which changes its operating state. Conventionally, axial fans or axial fans are used in such ventilation units, which are designed for the flow resistance of the heat exchanger without icing. As a result, the fan is operated only for a short time in the range of optimum efficiency, but with increasing icing of the heat exchanger and its increasing flow resistance, the operating state of the fan moves out of the range of optimum efficiency. Due to the increased flow resistance, the outflow direction also changes from an axial to a more and more radial direction.
Dabei ist neben der aus wirtschaftlicher Sicht verschlechterten Anlageneffizienz auch aus strömungstechnischer Sicht nachteilig, da sich die Wurfweite des Lüfters stark reduziert, wodurch es zu einer ungleichförmigen Temperaturverteilung in dem an den Lüfter angrenzenden Kühlraum kommt. Zudem wird radial ausgeblasene Luft anteilig direkt um den zunehmend vereisenden Wärmeübertrager zurück zu dessen Einlaufbereich gefördert und erneut durch den Wärmeübertrager hindurchgeführt, wodurch es zu einem thermischen Kurzschluss kommt.In addition to the deteriorated from an economic point of view system efficiency is also disadvantageous from a fluid engineering point of view, since the throwing distance of the fan is greatly reduced, resulting in a non-uniform temperature distribution in the adjoining the cooling fan room. In addition, radially blown air is proportionately conveyed directly to the increasingly icing heat exchanger back to the inlet region and again passed through the heat exchanger, resulting in a thermal short circuit.
Typischerweise befindet sich am Lüfter ausblasseitig ein Schutzgitter. In diesem Bereich mischt sich bei der zunehmend radialen Abströmung des Axiallüfters die sehr kalte Luft mit der Luft des angrenzenden Kühlraums (Rückströmung im Nabenbereich). In Anwendungen mit hoher Luftfeuchtigkeit kann sich Eis oder schneeähnliches Material an den Lüfterschaufeln oder dem Schutzgitter festsetzen, wodurch sich der Wirkungsgrad und die Strömungscharakteristik ebenfalls verschlechtern. Zudem kann beim Abtauen des Wärmeübertragers und stillstehendem Lüfter das Eis auf den Wandring des Lüfters fallen und durch Vereisung ein Wiederanlaufen des Lüfters verhindern.Typically, there is a protective grille on the exhaust side of the fan. In this area mixes with the increasingly radial outflow of the axial fan, the very cold air with the air of the adjacent refrigerator (backflow in the hub area). In high humidity applications, ice or snow-like material can adhere to the fan blades or guard, which also degrades efficiency and flow characteristics. In addition, when the heat exchanger defrosts and the fan is stationary, the ice can fall onto the wall ring of the fan and prevent the fan from restarting due to icing.
Das notwendige Abtauen ist generell ein nachteiliger, aufwendiger und so weit als möglich zu vermeidender Störungsprozess des eigentlichen Betriebs.The necessary defrosting is generally a disadvantageous, expensive and as far as possible avoidable disturbance process of the actual operation.
Der Erfindung liegt deshalb die Aufgabe zugrunde, eine Ventilationseinheit bereit zu stellen, welche die vorstehenden Nachteile überwindet und effizienter sowie mit geringerer Abtauhäufigkeit betrieben werden kann.The invention is therefore based on the object to provide a ventilation unit, which overcomes the above disadvantages and can be operated more efficiently and with a lower defrost frequency.
Diese Aufgabe wird durch die Merkmalskombination gemäß Patentanspruch 1 gelöst.This object is achieved by the feature combination according to
Erfindungsgemäß wird eine Ventilationseinheit ausgebildet zum Einsatz und zur Anordnung an einer Kälteanlage vorgeschlagen, mit einem Lüfter und einem zu dem Lüfter in Reihe angeordneten Wärmeübertrager, wobei der Lüfter ausgebildet und gegenüber dem Wärmeübertrager angeordnet ist, im Betrieb einen Luftvolumenstrom durch den Wärmeübertrager hindurch und aus der Ventilationseinheit heraus zu fördern. Der Lüfter ist erfindungsgemäß als Diagonallüfter ausgebildet. Bei dem Diagonallüfter wird der Luftvolumenstrom im Betrieb axial angesaugt und diagonal in einem Winkel gegenüber der Rotationsachse des Diagonallüfters ausgeblasen.According to the invention, a ventilation unit is designed for use and for arrangement on a refrigeration system, with a fan and a fan arranged in series in the heat exchanger, wherein the fan is formed and arranged opposite the heat exchanger, during operation, an air flow through the heat exchanger and out of the To promote ventilation unit out. The fan is inventively designed as a diagonal fan. In the diagonal fan, the air volume flow is sucked axially during operation and blown diagonally at an angle relative to the axis of rotation of the diagonal fan.
Der Diagonalventilator zeichnet sich in vorteilhafter Weise durch eine hohe Luftleistung auch bei höherem Gegendruck aus. Dabei ist sichergestellt, dass auch bei den im Betrieb maximal auftretenden Gegendrücken die Ausblasrichtung des Diagonalventilators stets diagonal und nicht radial ist. Seine Wurfweite bleibt auch bei einem kontinuierlich zunehmend vereisenden Wärmeübertrager im Wesentlichen unverändert groß, ein thermischer Kurzschluss durch eine außenseitige Rückströmung zum Ansaugbereich des Wärmeübertragers wird verhindert. Zudem wird eine sich hieraus ergebende stärkere Vereisung des Wärmeübertragers vermieden. Die Abtauzyklen des Wärmeübertragers werden verlängert.The diagonal fan is characterized in an advantageous manner by a high air flow even at higher back pressure. In this case, it is ensured that even with the counter pressures occurring maximally in the operation, the discharge direction of the diagonal fan is always diagonal and not radial. Its throwing distance remains essentially unchanged, even in the case of a continuously increasing heat exchanger, and a thermal short circuit through an outward return flow to the intake area of the heat exchanger is prevented. In addition, a resulting greater icing of the heat exchanger is avoided. The defrost cycles of the heat exchanger are extended.
In einer vorteilhaften Ausführungsvariante ist der Diagonallüfter ausgebildet, den Luftvolumenstrom axial anzusaugen und diagonal in einem Winkel von 10 - 80°, weiter bevorzugt einem Winkel von 25 - 60°, gegenüber seiner Rotationsachse auszublasen. Im Vergleich zu einem 0°-Ausblaswinkel eines Axiallüfters und einem 90°-Ausblaswinkel eines Radiallüfters bietet der Ausblaswinkel des Diagonallüfters von vorneherein einen Mittelwert, der über den Betrieb aufrecht erhalten werden kann.In an advantageous embodiment variant of the diagonal fan is designed to suck the air flow axially and diagonally at an angle of 10 - 80 °, more preferably an angle of 25 - 60 °, to blow out from its axis of rotation. Compared to a 0 ° blowing angle of an axial fan and a 90 ° blowing angle of a radial fan, the discharge angle of the diagonal fan a priori provides an average value which can be maintained over the operation.
Eine günstige Ausführungsform der Ventilationseinheit sieht vor, dass der Diagonallüfter ausgebildet und in der Ventilationseinheit angeordnet ist, den Luftvolumenstrom durch den Wärmeübertrager anzusaugen und aus der Ventilationseinheit heraus in eine freie Umgebung, beispielsweise in einem Kühlraum auszublasen. Der Diagonallüfter ist mithin strömungstechnisch dem Wärmeübertrager nachgeschaltet.A favorable embodiment of the ventilation unit provides that the diagonal fan is designed and arranged in the ventilation unit, to suck in the air volume flow through the heat exchanger and to blow it out of the ventilation unit into a free environment, for example in a cold room. The diagonal fan is therefore fluidly downstream of the heat exchanger.
Der Wärmeübertrager erzeugt im Betrieb durch fortschreitende Vereisung für den Diagonallüfter einen sich von einem Ausgangsströmungswiderstand mit einer ersten Widerstandskennlinie (A) zu einem Vereisungswiderstand mit einer zweiten Widerstandskennlinie (B) erhöhenden Durchströmungswiderstand. Bei der Ventilationseinheit ist eine vorteilhafte Ausführung dadurch gekennzeichnet, dass der Diagonallüfter ausgelegt ist, dass sein höchster Wirkungsgradbereich in einem Bereich einer dritten Widerstandskennlinie (C) des Wärmeübertragers ist, wobei die dritte Widerstandskennlinie zwischen der ersten und der zweiten Widerstandskennlinie (A, B) liegt. Die Widerstandskennlinien (A, B, C) sind dabei durch einen über eine geförderte Luftmenge qv [m3/h] ansteigenden Gegendruck psf [Pa] gekennzeichnet. Die Abströmung bleibt dabei auch bei maximalen Gegendrücken stets diagonal und verändert sich nicht in eine radiale Richtung, wie beispielsweise bei Axiallüftern.The heat exchanger generates in operation by progressive icing for the diagonal fan from a Ausgangsströmungswiderstand having a first resistance characteristic (A) to an icing resistance with a second resistance characteristic (B) increasing flow resistance. In the ventilation unit, an advantageous embodiment is characterized in that the diagonal fan is designed such that its highest efficiency range is in a range of a third resistance characteristic (C) of the heat exchanger, the third resistance characteristic lying between the first and the second resistance characteristic (A, B) , The resistance characteristic curves (A, B, C) are characterized by a backpressure psf [Pa] increasing over a conveyed air volume qv [m 3 / h]. The outflow remains always diagonal even at maximum back pressures and does not change in a radial direction, such as axial fans.
Erfindungsgemäß ist der Wärmeübertrager ausgebildet, den Luftvolumenstrom auf eine Fördermitteltemperatur von kleiner oder gleich 15°C, insbesondere 5°C zur Bildung eines Kaltluftvolumenstroms abzukühlen, wobei der Kaltluftvolumenstrom unmittelbar von dem Diagonallüfter ansaugbar und ausblasbar ist. Zwischen dem Wärmeübertrager und dem Diagonallüfter sind keine den Kaltluftvolumenstrom wärmetechnisch beeinflussenden Bauteile vorgesehen, die Ansaugung durch den Diagonallüfter erfolgt unmittelbar dem Wärmeübertrager nachgeschaltet.According to the invention, the heat exchanger is designed, the air volume flow to cool to a conveyor temperature of less than or equal to 15 ° C, in particular 5 ° C to form a cold air flow rate, the cold air flow is directly sucked and blown by the diagonal fan. Between the heat exchanger and the diagonal fan no cold air volume flow thermally influencing components are provided, the suction through the diagonal fan is directly downstream of the heat exchanger.
Die Ventilationseinheit ist in einer Weiterbildung dadurch gekennzeichnet, dass der Diagonallüfter und der Wärmeübertrager durch ein Gehäuse miteinander verbunden sind, wobei das Gehäuse einen geschlossenen Strömungskanal für den Luftvolumenstrom bzw. den Kaltluftvolumenstrom bildet.In a further development, the ventilation unit is characterized in that the diagonal fan and the heat exchanger are connected to one another by a housing, wherein the housing forms a closed flow channel for the air volume flow or the cold air volume flow.
Ferner ist auch vorteilhaft, dass die Ventilationseinheit als integrale Baueinheit zur ganzheitlichen Anordnung und Befestigung an der Kälteanlage ausgebildet ist. Die integrale Baueinheit kann als Ganzes vormontiert und geliefert werden. An den Kühlräumen muss lediglich noch der elektrische Anschluss erfolgen. Die Fehlerwahrscheinlichkeit bei der Montage wird hierdurch verringert.Furthermore, it is also advantageous that the ventilation unit is designed as an integral unit for the holistic arrangement and attachment to the refrigeration system. The integral assembly can be pre-assembled and delivered as a whole. At the cold rooms only the electrical connection has to be done. The error probability during assembly is thereby reduced.
In einer vorteilhaften Ausführungsvariante ist der Wärmeübertrager als Verdampfer ausgebildet.In an advantageous embodiment, the heat exchanger is designed as an evaporator.
Bei einer Weiterbildung umfasst die Ventilationseinheit ferner eine (Strömungs-)Leiteinrichtung, welche in einem Ausblasabschnitt des Diagonallüfters angeordnet und ausgebildet ist, den von dem Diagonallüfter in diagonaler Richtung ausgeblasenen Luftvolumenstrom in eine axiale Richtung umzulenken. Die diagonale Ausblasrichtung des Diagonallüfters kann hierdurch in eine axiale Ausblasströmungsrichtung umgelenkt und mithin die Wurfweite des Diagonallüfters vergrößert werden. Die Leiteinrichtung kann durch Teile des Gehäuses oder durch zusätzlich an dem Diagonallüfter befestigbare Leitkörper wie Leitbleche oder dergleichen realisiert werden. In einer Ausführungsvariante wird die Leiteinrichtung einteilig an dem Diagonallüfter ausgebildet, so dass die Teileanzahl minimiert ist.In a further development, the ventilation unit further comprises a (flow) guide device, which is arranged in a blow-out section of the diagonal fan and designed to deflect the volume of air blown from the diagonal fan in the diagonal direction in an axial direction. The diagonal discharge direction of the diagonal fan can thereby be deflected in an axial Ausblasströmungsrichtung and thus the throw of the diagonal fan can be increased. The guide device can be realized by parts of the housing or by additionally attachable to the diagonal fan guide body such as baffles or the like. In a variant the guide is integrally formed on the diagonal fan, so that the number of parts is minimized.
Ausblasseitig kann an dem Diagonallüfter zusätzlich ein Schutzgitter oder Eingriffsschutz angeordnet werden.Ausblasseitig can be arranged on the diagonal fan in addition a protective grid or intervention protection.
Ferner kann bei der Ventilationseinheit vorgesehen werden, dass die Leiteinrichtung den Drall des von dem Diagonallüfter erzeugten Luftvolumenstroms teilweise in statischen Druck umwandelt und dadurch die Druckerhöhung, Effizienz und Wurfweite des Diagonallüfters steigert.Furthermore, it can be provided in the ventilation unit that the guide partially converts the swirl of the air volume flow generated by the diagonal fan into static pressure and thereby increases the pressure increase, efficiency and throw of the diagonal fan.
Ferner ist der Diagonallüfter in einer Ausführungsvariante mit einer mitrotierenden, die Lüfterschaufeln überdeckenden Deckscheibe ausgebildet.Further, the diagonal fan is formed in a variant with a co-rotating, the fan blades covering the cover plate.
Der Ventilationseinheit kann zudem in einem Ausführungsbeispiel ferner derart ausgebildet sein, dass die Strömungsführung in dem feststehenden Gehäuse erfolgt und der Diagonallüfter ein axiallüfterähnliches Flügelende aufweist. Zwischen dem Laufrad und den Lüfterschaufeln ist dann ein Spalt vorgesehen.In one embodiment, the ventilation unit can furthermore be designed in such a way that the flow guidance takes place in the stationary housing and the diagonal fan has an axial fan-like wing end. Between the impeller and the fan blades then a gap is provided.
Andere vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet bzw. werden nachstehend zusammen mit der Beschreibung der bevorzugten Ausführung der Erfindung anhand der Figuren näher dargestellt. Es zeigen:
- Fig. 1
- eine nicht zur Erfindung gehörige Ventilationseinheit mit einem Axiallüfter gemäß dem Stand der Technik zur Veranschaulichung des Strömungsverhaltens im vereisten Zustand;
- Fig. 2
- die Ventilationseinheit aus
Fig. 1 in einem Zustand ohne Vereisung; - Fig. 3
- eine erfindungsgemäße Ventilationseinheit im vereisten Zustand;
- Fig. 4
- ein Diagramm zur Darstellung der Auslegung der erfindungsgemäßen Ventilationseinheit
- Fig. 1
- a ventilation unit not belonging to the invention with an axial fan according to the prior art for illustrating the flow behavior in the icy state;
- Fig. 2
- the ventilation unit off
Fig. 1 in a condition without icing; - Fig. 3
- a ventilation unit according to the invention in the icy state;
- Fig. 4
- a diagram illustrating the design of the ventilation unit according to the invention
In
In
Im Betrieb saugt der Diagonallüfter 2 einen Luftvolumenstrom aus axialer Richtung durch den Wärmeübertrager 3 hindurch an und bläst ihn trotz Vereisung anschließend aus der Ventilationseinheit 1 diagonal in einem Winkel a=30° gegenüber der Rotationsachse RA des Diagonallüfters 2 heraus in die freie Umgebung, beispielsweise in eine Kühlkammer. Der diagonale Abströmweg 7 ist mit Pfeilen gekennzeichnet.In operation, the
Der Wärmeübertrager 3 kühlt den Luftvolumenstrom auf eine Fördermitteltemperatur von kleiner oder gleich 15°C, insbesondere kleiner oder gleich 5°C, zur Bildung des Kaltluftvolumenstroms, der unmittelbar von dem Diagonallüfter 2 angesaugt wird.The
Die erfindungsgemäße Ventilationseinheit 1 gemäß
Der Durchströmungswiderstand des Wärmeübertragers 3 steigt im Betrieb durch fortschreitende Vereisung von einem Ausgangsströmungswiderstand mit einer ersten Widerstandskennlinie A für den Diagonallüfter zu einem Vereisungswiderstand mit einer zweiten Widerstandskennlinie B an. Im Zustand der zweiten Widerstandskennlinie wird ein Abtauprozess des Wärmeübertragers 3 eingeleitet. Der Diagonallüfter 2 ist hingegen durch seine diagonale Ausblasrichtung so ausgelegt, seinen höchsten Wirkungsgradbereich in einem Bereich der dritten Widerstandskennlinie C des Wärmeübertragers 3 aufzuweisen, wobei die dritte Widerstandskennlinie C zwischen der ersten und zweiten Widerstandskennlinie A, B liegt. Die Widerstandskennlinien A, B, C sind durch einen über eine geförderte Luftmenge qv [m3/h] ansteigenden Gegendruck psf [Pa] gekennzeichnet.The flow resistance of the
Die erfindungsgemäße Ventilationseinheit 1 mit dem Diagonallüfter 2 kann im Vergleich zu einem Aufbau mit dem Axiallüfter 11, der nur im Bereich der Widerstandskennlinie A auslegungsgemäß funktioniert, über einen längeren Zeitraum und mit höherem Wirkungsgrad im Bereich der Widerstandskennlinie C bei entsprechend gleich großer Fördermenge betrieben werden. Der absolute Unterschied ist durch die Lüfterkennlinien 11', 2' der Axiallüfter 11 und Diagonallüfter 2 im Diagramm gekennzeichnet.The
Claims (12)
Applications Claiming Priority (1)
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DE102017111001.1A DE102017111001A1 (en) | 2017-05-19 | 2017-05-19 | Ventilation unit for refrigeration systems |
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EP3404268A1 true EP3404268A1 (en) | 2018-11-21 |
EP3404268B1 EP3404268B1 (en) | 2023-02-01 |
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EP18172026.9A Active EP3404268B1 (en) | 2017-05-19 | 2018-05-14 | Ventilation unit for refrigeration systems |
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US (1) | US20180335244A1 (en) |
EP (1) | EP3404268B1 (en) |
CN (1) | CN207050304U (en) |
DE (1) | DE102017111001A1 (en) |
DK (1) | DK3404268T3 (en) |
ES (1) | ES2942180T3 (en) |
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DE102018211808A1 (en) * | 2018-07-16 | 2020-01-16 | Ziehl-Abegg Se | Fan and control device for a fan |
DE102018132002A1 (en) * | 2018-12-12 | 2020-06-18 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Ventilation unit |
US11371761B2 (en) * | 2020-04-13 | 2022-06-28 | Haier Us Appliance Solutions, Inc. | Method of operating an air conditioner unit based on airflow |
Citations (2)
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JP2003106742A (en) * | 2001-10-01 | 2003-04-09 | Toshiba Corp | Refrigerator |
EP2679920A2 (en) * | 2012-06-28 | 2014-01-01 | Samsung Electronics Co., Ltd | Indoor unit of air conditioner and method of controlling the air conditioner |
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JPS5163261U (en) * | 1974-11-13 | 1976-05-18 | ||
DE3914242C2 (en) * | 1989-04-29 | 1994-01-27 | Gea Happel Klimatechnik | Device for heating and / or cooling rooms |
KR100471444B1 (en) * | 2002-08-14 | 2005-03-08 | 엘지전자 주식회사 | The axial flow fan with turbo blades |
US7632073B2 (en) * | 2005-06-08 | 2009-12-15 | Dresser-Rand Company | Impeller with machining access panel |
WO2010070889A1 (en) * | 2008-12-15 | 2010-06-24 | ダイキン工業株式会社 | Air conditioning indoor unit embedded in ceiling |
US9086075B2 (en) * | 2011-07-07 | 2015-07-21 | Pentair Water Pool And Spa, Inc. | Impeller assembly and method |
DE102015207800A1 (en) * | 2015-04-28 | 2016-11-03 | Ziehl-Abegg Se | Diagonal or centrifugal fan, guide for such a fan and system with such a fan or with several such fans |
KR102403728B1 (en) * | 2015-10-07 | 2022-06-02 | 삼성전자주식회사 | Turbofan for air conditioning apparatus |
US10514046B2 (en) * | 2015-10-09 | 2019-12-24 | Carrier Corporation | Air management system for the outdoor unit of a residential air conditioner or heat pump |
DE102016111136A1 (en) * | 2016-06-17 | 2017-12-21 | Güntner Gmbh & Co. Kg | Air cooler for cooling the air in rooms, especially in walk-in storage or cold storage rooms |
-
2017
- 2017-05-19 DE DE102017111001.1A patent/DE102017111001A1/en not_active Withdrawn
- 2017-07-24 CN CN201720898493.4U patent/CN207050304U/en active Active
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2018
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- 2018-05-14 EP EP18172026.9A patent/EP3404268B1/en active Active
- 2018-05-14 DK DK18172026.9T patent/DK3404268T3/en active
- 2018-05-18 US US15/983,232 patent/US20180335244A1/en active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003106742A (en) * | 2001-10-01 | 2003-04-09 | Toshiba Corp | Refrigerator |
EP2679920A2 (en) * | 2012-06-28 | 2014-01-01 | Samsung Electronics Co., Ltd | Indoor unit of air conditioner and method of controlling the air conditioner |
Also Published As
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DE102017111001A1 (en) | 2018-11-22 |
CN207050304U (en) | 2018-02-27 |
ES2942180T3 (en) | 2023-05-30 |
US20180335244A1 (en) | 2018-11-22 |
EP3404268B1 (en) | 2023-02-01 |
DK3404268T3 (en) | 2023-04-03 |
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