US20180335244A1 - Ventilation Unit For Refrigeration Plants - Google Patents
Ventilation Unit For Refrigeration Plants Download PDFInfo
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- US20180335244A1 US20180335244A1 US15/983,232 US201815983232A US2018335244A1 US 20180335244 A1 US20180335244 A1 US 20180335244A1 US 201815983232 A US201815983232 A US 201815983232A US 2018335244 A1 US2018335244 A1 US 2018335244A1
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- Prior art keywords
- fan
- ventilation unit
- designed
- heat exchanger
- air volume
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- 238000009423 ventilation Methods 0.000 title claims abstract description 47
- 238000005057 refrigeration Methods 0.000 title claims abstract description 10
- 238000009434 installation Methods 0.000 claims abstract description 6
- 230000000750 progressive effect Effects 0.000 claims description 3
- 230000003068 static effect Effects 0.000 claims description 2
- 230000001681 protective effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004888 barrier function Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000011900 installation process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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 disclosure relates to a ventilation unit designed for installation and use at a refrigeration plant.
- a protective grille is located at the blowout side of the fan.
- the very cold air mixes with the air of the adjoining cold room (back flow in the hub region).
- ice or snowlike material may become deposited on the fan blades or the protective grille. This likewise worsens the efficiency and the flow characteristics.
- the ice may drop onto the wall ring of the fan and prevent a restarting of the fan due to frosting.
- the necessary defrosting is generally a disadvantageous and costly disruption of the proper operation, one to be avoided as much as possible.
- the problem that the disclosure proposes to solve is, therefore, to provide a ventilation unit that overcomes the above drawbacks and can be operated more efficiently, as well as with less frequent defrosting.
- the ventilation unit designed for installation and use at a refrigeration plant.
- the ventilation unit includes a fan and a heat exchanger, arranged in series with the fan.
- the fan is designed and positioned with regard to the heat exchanger so as to deliver, in operation, an air volume that flows through the heat exchanger and out from the ventilation unit.
- the fan is designed as a diagonal fan.
- the diagonal fan axially draws in the air volume flow during operation and blows it out diagonally at an angle relative to its axis of rotation (RA).
- the heat exchanger is designed to cool the air volume flow down to a mean delivery temperature of ⁇ 15° C. in order to form a cold air volume.
- the cold air volume flow can be directly drawn in and blown out by the diagonal fan.
- a ventilation unit is designed for installation and use at a refrigeration plant.
- a fan and a heat exchanger are arranged in series with the fan.
- the fan is designed and positioned with regard to the heat exchanger so as to deliver, in operation, an air volume flow through the heat exchanger and out the ventilation unit.
- the fan is designed according to the disclosure as a diagonal fan. In the diagonal fan, the air volume flow during operation is drawn in axially and blown out diagonally at an angle relative to the axis of rotation of the diagonal fan.
- the diagonal ventilator is advantageously distinguished by a high air output even with large backpressure. This ensures that the blowout direction of the diagonal ventilator is always diagonal and not radial, even if maximum backpressures occurs during operation. Its throw also remains substantially the same without change, even with a continuously increasingly frosted heat exchanger. Thus, a thermal short circuit is prevented due to backflow at the outlet to the intake zone of the heat exchanger. Furthermore, this prevents a further frosting of the heat exchanger as a result. The defrost cycles of the heat exchanger become longer.
- the diagonal fan is designed to draw in the air volume flow axially and to blow it out diagonally at an angle of 10-80°, and, more preferably, at an angle of 25-60° with respect to its axis of rotation.
- the blowout angle of the diagonal fan affords a middle value from the outset, that can be maintained throughout the operation.
- the ventilation unit proposes that the diagonal fan is designed to draw in the air volume flow axially through the heat exchanger and to blow it out from the ventilation unit into the free surroundings, for example in a cold room.
- the diagonal fan is therefore fluidically connected downstream from the heat exchanger.
- the heat exchanger generates, by progressive frosting for the diagonal fan during operation, a flow resistance increasing from a starting flow resistance with a first resistance characteristic (A) to a frosting resistance with a second resistance characteristic (B).
- One advantageous embodiment of the ventilation unit is characterized in that the diagonal fan is designed to have its highest efficiency range in an area of a third resistance characteristic (C) of the heat exchanger.
- the third resistance characteristic lies between the first and the second resistance characteristic (A, B).
- the resistance characteristics (A, B, C) are characterized by an increasing backpressure psf [Pa] plotted against a delivered air quantity qv [m3/h].
- the outflow even at maximum backpressures, also always remains diagonal and does not change in a radial direction, such as with axial fans.
- the heat exchanger is designed to cool the air volume flow down to a mean delivery temperature less than or equal to 15° C., especially 5° C., in order to form a cold air volume.
- the cold air volume flow can be directly drawn in and blown out by the diagonal fan. Between the heat exchanger and the diagonal fan there are no components thermally influencing the cold air volume flow. The intake by the diagonal fan occurs immediately downstream from the heat exchanger.
- the ventilation unit in one embodiment is characterized in that the diagonal fan and the heat exchanger are joined together by a housing. This forms a closed flow duct for the air volume flow or the cold air volume flow.
- the ventilation unit is also advantageous for the ventilation unit to be designed as an integrated structural unit for complete arrangement and fastening on the refrigeration plant.
- the integrated component can be pre-assembled as a whole and delivered. At the cold room, only the electrical hook-up needs to be done. This reduces the likelihood of mistakes during the installation process.
- the heat exchanger is designed as an evaporator.
- the ventilation unit moreover comprises a flow guide device. It is arranged in a blowout portion of the diagonal fan and is designed to deflect the air volume flow blown out by the diagonal fan in a diagonal direction into an axial direction.
- the diagonal blowout direction of the diagonal fan may in this way be diverted into an axial blowout direction.
- the throw of the diagonal fan is increased.
- the guide device can be realized by parts of the housing or by guiding bodies secured additionally on the diagonal fan, such as air baffles or the like.
- the guide device is designed as a single piece on the diagonal fan. Thus, the number of parts is minimized.
- a protective grille or access barrier may be arranged on the diagonal fan at the blowout side.
- the guide device transforms the spin of the air volume flow produced by the diagonal fan partly into static pressure and thereby boosts the pressure increase, efficiency, and throw of the diagonal fan.
- the diagonal fan has a co-rotating cover disk covering the fan blades.
- the ventilation unit in one sample embodiment may furthermore be designed such that the flow guidance occurs in the stationary housing and the diagonal fan has an axial fanlike wing tip. A gap is then formed between the impeller and the fan blades.
- FIG. 1 is a cross-section schematic view of a ventilation unit not pertaining to the disclosure with an axial fan of the prior art to illustrate the flow behavior in the frosted state;
- FIG. 2 is a cross-section schematic view of the ventilation unit of FIG. 1 in a state without frosting;
- FIG. 3 is a cross-section schematic view of a ventilation unit according to the disclosure in the frosted state.
- FIG. 4 is a diagram to show the design of the ventilation unit according to the disclosure.
- FIG. 1 shows the basic schematic layout of the ventilation unit according to the disclosure, but with an axial fan 11 connected to a heat exchanger 10 , in order to illustrate the fluidic problems.
- FIG. 1 shows a frosted state of the heat exchanger 10 and a resulting substantially radial outflow of the axial fan 11 .
- a thermal short circuit is produced on the flow path 8 represented by arrows. Air is blown out from the axial fan 11 and returns once more to the intake zone of the heat exchanger.
- an inflow 9 occurs at the blowout side in the hub zone of the axial fan 11 , on which the outflow is superimposed.
- the frosted state of the heat exchanger little or nothing remains of the actual purely axial outflow provided in the nonfrosted state, as shown for example in FIG. 2 .
- FIG. 3 shows schematically a ventilation unit 1 according to the disclosure in the frosted state with a diagonal fan 2 and a heat exchanger 3 , designed as an evaporator, arranged in series with it.
- the heat exchanger 3 and the diagonal fan are joined together by a housing 5 .
- the housing 5 forms a flow duct.
- Both the diagonal fan 2 and the heat exchanger 3 are installed and secured in the housing 5 .
- the ventilation unit is an integrated structural unit.
- a protective grille is arranged on the blowout portion of the diagonal ventilator 2 .
- the ventilation unit 1 in its schematically represented form is designed for installation and use at a refrigeration plant.
- the diagonal fan 2 draws in an air volume flow from the axial direction through the heat exchanger 3 .
- the diagonal outflow path 7 is indicated by arrows.
- the heat exchanger 3 cools the air volume flow down to a mean delivery temperature equal to or less than 15° C., especially equal to or less than 5° C., in order to form the cold air volume flow, which is taken in directly by the diagonal fan 2 .
- the ventilation unit 1 according to the disclosure in FIG. 3 with the diagonal fan 2 may be interpreted, as compared to the embodiment with an axial fan 10 represented in FIG. 1 , in the manner shown in FIG. 4 with the aid of a diagram of the delivered air volume qv [m3/h] plotted against the pressure psf [Pa].
- the fan characteristics 11 ′, 2 ′ of the axial fan 11 of FIG. 1 , the diagonal fan 2 of FIG. 3 , as well as three resistance characteristic curves A, B, C due to different frosting states of the heat exchanger 3 are plotted in FIG. 4 .
- the flow resistance of the heat exchanger 3 increases during operation by progressive frosting from a starting flow resistance with a first resistance characteristic A for the diagonal fan to a frosting resistance with a second resistance characteristic B.
- a defrosting process is initiated for the heat exchanger 3 .
- the diagonal fan 2 is designed such by its diagonal blowout direction that it has its highest efficiency range in a region of the third resistance characteristic C of the heat exchanger 3 .
- the third resistance characteristic C lies between the first and second resistance characteristic A, B.
- the resistance characteristics A, B, C are characterized by an increasing backpressure psf [Pa] plotted against the delivered air volume qv [m3/h].
- the ventilation unit 1 according to the disclosure with the diagonal fan 2 can be operated for a longer time and with higher efficiency in the region of the resistance characteristic C for the same corresponding delivery volume, as compared to a layout with the axial fan 11 .
- the axial fan 11 only functions per design in the region of the resistance characteristic A.
- the absolute difference is indicated in the diagram by the fan characteristic curves 11 ′, 2 ′ of the axial fan 11 and diagonal fan 2 .
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- Engineering & Computer Science (AREA)
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- 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
Description
- This application claims priority to German Application No. 102017111001.1, filed May 19, 2017. The disclosures of the above application is incorporating herein by reference.
- The disclosure relates to a ventilation unit designed for installation and use at a refrigeration plant.
- One problem, at refrigeration plants, with the use of ventilation units having fans and heat transfer units, often called heat exchangers, is the fact that the heat exchanger becomes continuously frosted during its operation. Therefore, flow resistance increases. The downstream fan must work against the increasing flow resistance, so that its operating state is altered. Traditionally, axial fans or axial ventilators are used in such ventilation units. They are designed for flow resistance of the heat exchanger without frosting. As a result, the fan is only operated for a short time in the range of optimal efficiency. However, with increasing frosting of the heat exchanger and its increasing flow resistance, the operating state of the fan is moved away from the optimal efficiency range. Furthermore, due to the increased flow resistance, the outflow direction changes from an axial to an increasingly radial direction.
- Besides the worse plant efficiency in economic terms, it is also a disadvantage from the standpoint of fluidics, since the throw of the fan is greatly reduced, resulting in an uneven temperature distribution in the cold room adjacent to the fan. Furthermore, radially blown air is partly delivered around the increasingly frosted heat exchanger and back to its inlet zone. Once again, the air is taken through the heat exchanger and produces a thermal short circuit.
- Typically, a protective grille is located at the blowout side of the fan. In this zone, with increasing radial outflow of the axial fan, the very cold air mixes with the air of the adjoining cold room (back flow in the hub region). In applications with high humidity, ice or snowlike material may become deposited on the fan blades or the protective grille. This likewise worsens the efficiency and the flow characteristics. Furthermore, when the heat exchanger is being defrosted and the fan is standing still, the ice may drop onto the wall ring of the fan and prevent a restarting of the fan due to frosting.
- The necessary defrosting is generally a disadvantageous and costly disruption of the proper operation, one to be avoided as much as possible.
- The problem that the disclosure proposes to solve is, therefore, to provide a ventilation unit that overcomes the above drawbacks and can be operated more efficiently, as well as with less frequent defrosting.
- This problem is solved by a ventilation unit designed for installation and use at a refrigeration plant. The ventilation unit includes a fan and a heat exchanger, arranged in series with the fan. The fan is designed and positioned with regard to the heat exchanger so as to deliver, in operation, an air volume that flows through the heat exchanger and out from the ventilation unit. The fan is designed as a diagonal fan. The diagonal fan axially draws in the air volume flow during operation and blows it out diagonally at an angle relative to its axis of rotation (RA). The heat exchanger is designed to cool the air volume flow down to a mean delivery temperature of ≤15° C. in order to form a cold air volume. The cold air volume flow can be directly drawn in and blown out by the diagonal fan.
- According to the disclosure, a ventilation unit is designed for installation and use at a refrigeration plant. A fan and a heat exchanger are arranged in series with the fan. The fan is designed and positioned with regard to the heat exchanger so as to deliver, in operation, an air volume flow through the heat exchanger and out the ventilation unit. The fan is designed according to the disclosure as a diagonal fan. In the diagonal fan, the air volume flow during operation is drawn in axially and blown out diagonally at an angle relative to the axis of rotation of the diagonal fan.
- The diagonal ventilator is advantageously distinguished by a high air output even with large backpressure. This ensures that the blowout direction of the diagonal ventilator is always diagonal and not radial, even if maximum backpressures occurs during operation. Its throw also remains substantially the same without change, even with a continuously increasingly frosted heat exchanger. Thus, a thermal short circuit is prevented due to backflow at the outlet to the intake zone of the heat exchanger. Furthermore, this prevents a further frosting of the heat exchanger as a result. The defrost cycles of the heat exchanger become longer.
- In one advantageous variant embodiment, the diagonal fan is designed to draw in the air volume flow axially and to blow it out diagonally at an angle of 10-80°, and, more preferably, at an angle of 25-60° with respect to its axis of rotation. As compared to a 0° blowout angle of an axial fan and a 90° blowout angle of a radial fan, the blowout angle of the diagonal fan affords a middle value from the outset, that can be maintained throughout the operation.
- One favorable embodiment of the ventilation unit proposes that the diagonal fan is designed to draw in the air volume flow axially through the heat exchanger and to blow it out from the ventilation unit into the free surroundings, for example in a cold room. The diagonal fan is therefore fluidically connected downstream from the heat exchanger.
- The heat exchanger generates, by progressive frosting for the diagonal fan during operation, a flow resistance increasing from a starting flow resistance with a first resistance characteristic (A) to a frosting resistance with a second resistance characteristic (B). One advantageous embodiment of the ventilation unit is characterized in that the diagonal fan is designed to have its highest efficiency range in an area of a third resistance characteristic (C) of the heat exchanger. The third resistance characteristic lies between the first and the second resistance characteristic (A, B). The resistance characteristics (A, B, C) are characterized by an increasing backpressure psf [Pa] plotted against a delivered air quantity qv [m3/h]. The outflow, even at maximum backpressures, also always remains diagonal and does not change in a radial direction, such as with axial fans.
- According to the disclosure, the heat exchanger is designed to cool the air volume flow down to a mean delivery temperature less than or equal to 15° C., especially 5° C., in order to form a cold air volume. The cold air volume flow can be directly drawn in and blown out by the diagonal fan. Between the heat exchanger and the diagonal fan there are no components thermally influencing the cold air volume flow. The intake by the diagonal fan occurs immediately downstream from the heat exchanger.
- The ventilation unit in one embodiment is characterized in that the diagonal fan and the heat exchanger are joined together by a housing. This forms a closed flow duct for the air volume flow or the cold air volume flow.
- Moreover, it is also advantageous for the ventilation unit to be designed as an integrated structural unit for complete arrangement and fastening on the refrigeration plant. The integrated component can be pre-assembled as a whole and delivered. At the cold room, only the electrical hook-up needs to be done. This reduces the likelihood of mistakes during the installation process.
- In one advantageous embodiment, the heat exchanger is designed as an evaporator.
- In one modification, the ventilation unit moreover comprises a flow guide device. It is arranged in a blowout portion of the diagonal fan and is designed to deflect the air volume flow blown out by the diagonal fan in a diagonal direction into an axial direction. The diagonal blowout direction of the diagonal fan may in this way be diverted into an axial blowout direction. Hence, the throw of the diagonal fan is increased. The guide device can be realized by parts of the housing or by guiding bodies secured additionally on the diagonal fan, such as air baffles or the like. In one variant embodiment, the guide device is designed as a single piece on the diagonal fan. Thus, the number of parts is minimized.
- In addition, a protective grille or access barrier may be arranged on the diagonal fan at the blowout side.
- Moreover, it may be provided, in the ventilation unit, that the guide device transforms the spin of the air volume flow produced by the diagonal fan partly into static pressure and thereby boosts the pressure increase, efficiency, and throw of the diagonal fan.
- Moreover, in one variant embodiment the diagonal fan has a co-rotating cover disk covering the fan blades.
- The ventilation unit in one sample embodiment may furthermore be designed such that the flow guidance occurs in the stationary housing and the diagonal fan has an axial fanlike wing tip. A gap is then formed between the impeller and the fan blades.
- Other advantageous modifications of the disclosure will be presented in further detail below, together with the description of the preferred embodiment of the invention with the aid of the figures.
-
FIG. 1 is a cross-section schematic view of a ventilation unit not pertaining to the disclosure with an axial fan of the prior art to illustrate the flow behavior in the frosted state; -
FIG. 2 is a cross-section schematic view of the ventilation unit ofFIG. 1 in a state without frosting; -
FIG. 3 is a cross-section schematic view of a ventilation unit according to the disclosure in the frosted state; and -
FIG. 4 is a diagram to show the design of the ventilation unit according to the disclosure. -
FIG. 1 shows the basic schematic layout of the ventilation unit according to the disclosure, but with anaxial fan 11 connected to aheat exchanger 10, in order to illustrate the fluidic problems.FIG. 1 shows a frosted state of theheat exchanger 10 and a resulting substantially radial outflow of theaxial fan 11. A thermal short circuit is produced on theflow path 8 represented by arrows. Air is blown out from theaxial fan 11 and returns once more to the intake zone of the heat exchanger. Furthermore, an inflow 9 occurs at the blowout side in the hub zone of theaxial fan 11, on which the outflow is superimposed. In the frosted state of the heat exchanger, little or nothing remains of the actual purely axial outflow provided in the nonfrosted state, as shown for example inFIG. 2 . -
FIG. 3 shows schematically a ventilation unit 1 according to the disclosure in the frosted state with adiagonal fan 2 and aheat exchanger 3, designed as an evaporator, arranged in series with it. Theheat exchanger 3 and the diagonal fan are joined together by ahousing 5. Thehousing 5 forms a flow duct. Both thediagonal fan 2 and theheat exchanger 3 are installed and secured in thehousing 5. Thus, the ventilation unit is an integrated structural unit. On the blowout portion of thediagonal ventilator 2, a protective grille is arranged. The ventilation unit 1 in its schematically represented form is designed for installation and use at a refrigeration plant. - In operation, the
diagonal fan 2 draws in an air volume flow from the axial direction through theheat exchanger 3. The diagonal fans blows out the air despite frosting, from the ventilation unit 1 diagonally in an angle α=30° with respect to the axis of rotation RA of thediagonal fan 2 into the open surroundings, such as a cold chamber. Thediagonal outflow path 7 is indicated by arrows. - The
heat exchanger 3 cools the air volume flow down to a mean delivery temperature equal to or less than 15° C., especially equal to or less than 5° C., in order to form the cold air volume flow, which is taken in directly by thediagonal fan 2. - The ventilation unit 1 according to the disclosure in
FIG. 3 with thediagonal fan 2 may be interpreted, as compared to the embodiment with anaxial fan 10 represented inFIG. 1 , in the manner shown inFIG. 4 with the aid of a diagram of the delivered air volume qv [m3/h] plotted against the pressure psf [Pa]. Thefan characteristics 11′, 2′ of theaxial fan 11 ofFIG. 1 , thediagonal fan 2 ofFIG. 3 , as well as three resistance characteristic curves A, B, C due to different frosting states of theheat exchanger 3, are plotted inFIG. 4 . - The flow resistance of the
heat exchanger 3 increases during operation by progressive frosting from a starting flow resistance with a first resistance characteristic A for the diagonal fan to a frosting resistance with a second resistance characteristic B. In the state of the second resistance characteristic, a defrosting process is initiated for theheat exchanger 3. Thediagonal fan 2, on the other hand, is designed such by its diagonal blowout direction that it has its highest efficiency range in a region of the third resistance characteristic C of theheat exchanger 3. The third resistance characteristic C lies between the first and second resistance characteristic A, B. The resistance characteristics A, B, C are characterized by an increasing backpressure psf [Pa] plotted against the delivered air volume qv [m3/h]. - The ventilation unit 1 according to the disclosure with the
diagonal fan 2 can be operated for a longer time and with higher efficiency in the region of the resistance characteristic C for the same corresponding delivery volume, as compared to a layout with theaxial fan 11. Theaxial fan 11 only functions per design in the region of the resistance characteristic A. The absolute difference is indicated in the diagram by the fancharacteristic curves 11′, 2′ of theaxial fan 11 anddiagonal fan 2.
Claims (13)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017111001.1A DE102017111001A1 (en) | 2017-05-19 | 2017-05-19 | Ventilation unit for refrigeration systems |
DE102017111001.1 | 2017-05-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20180335244A1 true US20180335244A1 (en) | 2018-11-22 |
Family
ID=61497789
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/983,232 Pending US20180335244A1 (en) | 2017-05-19 | 2018-05-18 | Ventilation Unit For Refrigeration Plants |
Country Status (6)
Country | Link |
---|---|
US (1) | US20180335244A1 (en) |
EP (1) | EP3404268B1 (en) |
CN (1) | CN207050304U (en) |
DE (1) | DE102017111001A1 (en) |
DK (1) | DK3404268T3 (en) |
ES (1) | ES2942180T3 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11359644B2 (en) * | 2018-07-16 | 2022-06-14 | Ziehl-Abegg Se | Ventilator and deflector plate for a ventilator |
US11371761B2 (en) * | 2020-04-13 | 2022-06-28 | Haier Us Appliance Solutions, Inc. | Method of operating an air conditioner unit based on airflow |
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DE102018132002A1 (en) * | 2018-12-12 | 2020-06-18 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Ventilation unit |
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2017
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- 2017-07-24 CN CN201720898493.4U patent/CN207050304U/en active Active
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2018
- 2018-05-14 ES ES18172026T patent/ES2942180T3/en active Active
- 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
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US20060280609A1 (en) * | 2005-06-08 | 2006-12-14 | Dresser-Rand Comapny | Impeller with machining access panel |
US20130011268A1 (en) * | 2011-07-07 | 2013-01-10 | James Miller | Impeller Assembly and Method |
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US11359644B2 (en) * | 2018-07-16 | 2022-06-14 | Ziehl-Abegg Se | Ventilator and deflector plate for a ventilator |
US11371761B2 (en) * | 2020-04-13 | 2022-06-28 | Haier Us Appliance Solutions, Inc. | Method of operating an air conditioner unit based on airflow |
Also Published As
Publication number | Publication date |
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DE102017111001A1 (en) | 2018-11-22 |
CN207050304U (en) | 2018-02-27 |
ES2942180T3 (en) | 2023-05-30 |
EP3404268A1 (en) | 2018-11-21 |
EP3404268B1 (en) | 2023-02-01 |
DK3404268T3 (en) | 2023-04-03 |
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