EP3404268B1 - Ventilationseinheit für kälteanlagen - Google Patents

Ventilationseinheit für kälteanlagen Download PDF

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Publication number
EP3404268B1
EP3404268B1 EP18172026.9A EP18172026A EP3404268B1 EP 3404268 B1 EP3404268 B1 EP 3404268B1 EP 18172026 A EP18172026 A EP 18172026A EP 3404268 B1 EP3404268 B1 EP 3404268B1
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EP
European Patent Office
Prior art keywords
fan
ventilation unit
designed
heat exchanger
air volume
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.)
Active
Application number
EP18172026.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3404268A1 (de
Inventor
Oliver Haaf
Thomas Heli
Daniel Gebert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ebm Papst Mulfingen GmbH and Co KG
Original Assignee
Ebm Papst Mulfingen GmbH and Co KG
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Publication date
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Publication of EP3404268A1 publication Critical patent/EP3404268A1/de
Application granted granted Critical
Publication of EP3404268B1 publication Critical patent/EP3404268B1/de
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Classifications

    • 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 invention relates to a ventilation unit designed for use and for arrangement in a refrigeration system.
  • a protective grille is typically located on the outlet side of the fan. In this area, the very cold air mixes with the air from the adjoining cooling chamber (return flow in the hub area) as the axial fan flows increasingly radially. In high humidity applications, ice or snow-like material can stick to the fan blades or protective grille, also reducing efficiency and flow characteristics. In addition, when the heat exchanger is defrosted and the fan is not running, the ice can fall onto the wall ring of the fan and prevent the fan from restarting due to icing.
  • the necessary defrosting is generally a disadvantageous, complex process that disrupts actual operation and should be avoided as far as possible.
  • the invention is therefore based on the object of providing a ventilation unit which overcomes the above disadvantages and can be operated more efficiently and with less defrosting frequency.
  • a ventilation unit designed for use and for arrangement on a refrigeration system with a fan and a heat exchanger arranged in series with the fan, with the fan being designed and arranged opposite the heat exchanger, during operation an air volume flow through the heat exchanger and out of the Promote ventilation unit out.
  • the fan is designed as a diagonal fan. With the diagonal fan, the air volume flow is sucked in axially during operation and blown out diagonally at an angle to the rotation axis of the diagonal fan.
  • the diagonal fan is characterized in an advantageous manner by a high air output even at higher back pressure. This ensures that the blow-out direction of the diagonal fan is always diagonal and not radial, even with the maximum counter-pressures that occur during operation. Its range of throw remains largely unchanged even with a continuously increasing icing heat exchanger, a thermal short circuit due to an external backflow to the intake area of the heat exchanger is prevented. In addition, the resultant increased icing of the heat exchanger is avoided. The defrost cycles heat exchanger are extended.
  • the diagonal fan is designed to draw in the air volume flow axially and blow it out diagonally at an angle of 10-80°, more preferably at an angle of 25-60°, relative to its axis of rotation.
  • the discharge angle of the diagonal fan offers an average value from the outset that can be maintained throughout operation.
  • a favorable embodiment of the ventilation unit provides that the diagonal fan is designed and arranged in the ventilation unit to draw in the air volume flow through the heat exchanger and blow it out of the ventilation unit into an open environment, for example in a cold room.
  • the diagonal fan is therefore downstream of the heat exchanger in terms of flow.
  • the heat exchanger During operation, the heat exchanger generates a flow resistance that increases from an initial flow resistance with a first resistance characteristic curve (A) to an icing resistance with a second resistance characteristic curve (B) due to progressive icing for the diagonal fan.
  • the diagonal fan In the case of the ventilation unit, an embodiment according to the invention is characterized in that the diagonal fan is designed so that its highest efficiency range is in a range of a third resistance characteristic (C) of the heat exchanger, with the third resistance characteristic lying between the first and the second resistance characteristic (A, B).
  • the resistance characteristics (A, B, C) are characterized by a back pressure psf [Pa] that increases over a conveyed air quantity qv [m 3 /h]. The outflow always remains diagonal, even at maximum counter pressures, and does not change in a radial direction, as is the case with axial fans, for example.
  • the heat exchanger is designed according to the invention, the air volume flow to a conveying medium temperature of less than or equal to 15°C, in particular 5°C, to form a cold air volume flow, the cold air volume flow being able to be sucked in and blown out directly by the diagonal fan. Between the heat exchanger and the diagonal fan there are no components that thermally influence the cold air volume flow, the suction through the diagonal fan takes place 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, the housing forming a closed flow channel for the air volume flow or the cold air volume flow.
  • the ventilation unit is designed as an integral structural unit for holistic arrangement and attachment to the refrigeration system.
  • the integral unit can be pre-assembled and delivered as a whole. Only the electrical connection has to be made to the cold rooms. This reduces the probability of errors during assembly.
  • the heat exchanger is designed as an evaporator.
  • the ventilation unit also includes a (flow) guide device which is arranged in a blow-out section of the diagonal fan and is designed to deflect the air volume flow blown out in a diagonal direction by the diagonal fan into an axial direction.
  • the diagonal blow-out direction of the diagonal fan can thereby be deflected into an axial blow-out flow direction and thus the throw of the diagonal fan can be increased.
  • the guide device can be implemented by parts of the housing or by guide bodies such as guide plates or the like that can also be fastened to the diagonal fan.
  • the guide device is formed in one piece on the diagonal fan, so that the number of parts is minimized.
  • a protective grille or access protection can also be arranged on the diagonal fan.
  • the guide device 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 designed with a co-rotating cover disk that covers the fan blades.
  • the ventilation unit can also be designed in such a way that the flow is guided in the fixed housing and the diagonal fan has a wing end similar to an axial fan. A gap is then provided between the impeller and the fan blades.
  • FIG 1 the basic inventive structure of the ventilation unit is shown schematically, but to illustrate the fluidic problems with an axial fan 11 following a heat exchanger 10. Shown is a frozen state of the heat exchanger 10 and a resulting essentially radial outflow of the axial fan 11. About the with The flow path 8 shown by the arrows leads to a thermal short circuit, in which the air blown out of the axial fan 11 returns to the intake area of the heat exchanger. In addition, there is an inflow 9 on the outlet side in the hub region of the axial fan 11, which is overlaid by the outflow. From the actual purely axial outflow provided in the frost-free state, as exemplified in figure 2 is shown, when the heat exchanger is iced up, there is nothing or hardly anything left.
  • a ventilation unit 1 is shown schematically in the iced state with a diagonal fan 2 and a heat exchanger 3 arranged in series therewith and designed as an evaporator.
  • the heat exchanger 3 and the diagonal fan are connected to one another via a housing 5 forming a flow channel. Both the diagonal fan 2 and the heat exchanger 3 are inserted and fastened in the housing 5, so that the ventilation unit is an integral structural unit.
  • a protective grille 19 is arranged on the outlet section of the diagonal fan 2 .
  • the ventilation unit 1 is designed for use and for arrangement in a refrigeration system.
  • the diagonal outflow path 7 is marked with arrows.
  • the heat exchanger 3 cools the air volume flow to a conveying medium 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 in directly by the diagonal fan 2 .
  • the ventilation unit 1 according to the invention figure 3 with the diagonal fan 2 is opposite to the in figure 1
  • the embodiment shown can be designed with an axial fan 10 in a way as is shown in figure 4 is shown using a diagram of the conveyed air volume qv [m 3 /h] versus the pressure psf [Pa].
  • the fan characteristics 11', 2' of the axial fan 11 are off figure 1 and the diagonal fan 2 off figure 3 and three characteristic resistance curves A, B, C resulting from different icing states of the heat exchanger 3.
  • the flow resistance of the heat exchanger 3 increases during operation due to progressive icing from an initial flow resistance with a first resistance characteristic A for the diagonal fan to an icing resistance with a second resistance characteristic B. In the state of the second resistance characteristic, a defrosting process of the heat exchanger 3 is initiated.
  • the diagonal fan 2 on the other hand, is designed to have its highest efficiency range in a region of the third resistance characteristic C of the heat exchanger 3 due to its diagonal blowing direction, with the third resistance characteristic C lying between the first and second resistance characteristic curves A, B.
  • the resistance characteristics A, B, C are characterized by a back pressure psf [Pa] that increases over a conveyed air quantity 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 area of the resistance characteristic C with a correspondingly large flow rate compared to a structure with the axial fan 11, which only works as designed in the area of the resistance characteristic curve A.
  • the absolute difference is characterized by the fan characteristics 11', 2' of the axial fan 11 and the 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)
EP18172026.9A 2017-05-19 2018-05-14 Ventilationseinheit für kälteanlagen Active EP3404268B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017111001.1A DE102017111001A1 (de) 2017-05-19 2017-05-19 Ventilationseinheit für Kälteanlagen

Publications (2)

Publication Number Publication Date
EP3404268A1 EP3404268A1 (de) 2018-11-21
EP3404268B1 true EP3404268B1 (de) 2023-02-01

Family

ID=61497789

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18172026.9A Active EP3404268B1 (de) 2017-05-19 2018-05-14 Ventilationseinheit für kälteanlagen

Country Status (6)

Country Link
US (1) US20180335244A1 (zh)
EP (1) EP3404268B1 (zh)
CN (1) CN207050304U (zh)
DE (1) DE102017111001A1 (zh)
DK (1) DK3404268T3 (zh)
ES (1) ES2942180T3 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018211808A1 (de) * 2018-07-16 2020-01-16 Ziehl-Abegg Se Ventilator und Leiteinrichtung für einen Ventilator
DE102018132002A1 (de) * 2018-12-12 2020-06-18 Ebm-Papst Mulfingen Gmbh & Co. Kg Ventilationseinheit
US11371761B2 (en) * 2020-04-13 2022-06-28 Haier Us Appliance Solutions, Inc. Method of operating an air conditioner unit based on airflow

Citations (1)

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Publication number Priority date Publication date Assignee Title
US20170102007A1 (en) * 2015-10-09 2017-04-13 Carrier Corporation Air management system for the outdoor unit of a residential air conditioner or heat pump

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JPS5163261U (zh) * 1974-11-13 1976-05-18
DE3914242C2 (de) * 1989-04-29 1994-01-27 Gea Happel Klimatechnik Einrichtung zum Erwärmen und/oder Kühlen von Räumen
JP2003106742A (ja) * 2001-10-01 2003-04-09 Toshiba Corp 冷蔵庫
KR100471444B1 (ko) * 2002-08-14 2005-03-08 엘지전자 주식회사 송풍팬
US7632073B2 (en) * 2005-06-08 2009-12-15 Dresser-Rand Company Impeller with machining access panel
CN103557561B (zh) * 2008-12-15 2016-01-13 大金工业株式会社 天花板埋入型空调室内机
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KR102403728B1 (ko) * 2015-10-07 2022-06-02 삼성전자주식회사 공기조화장치용 터보팬
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Publication number Priority date Publication date Assignee Title
US20170102007A1 (en) * 2015-10-09 2017-04-13 Carrier Corporation Air management system for the outdoor unit of a residential air conditioner or heat pump

Non-Patent Citations (2)

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Title
SANDERS C.T.: "FROST FORMATION: THE INFLUENCE OF FROST FORMATION AND DEFROSTING ON THE PERFORMANCE OF AIR COOLERS", 23 October 1974 (1974-10-23), XP055790804, Retrieved from the Internet <URL:https://repository.tudelft.nl/islandora/object/uuid%3Ab99381a0-893c-4382-8b14-b1d9bdb370dd> [retrieved on 20210329] *
SCHILD P.G. ET AL: "Recommendations on Specific Fan Power and Fan System Efficiency", 31 December 2009 (2009-12-31), XP055790794, Retrieved from the Internet <URL:https://www.aivc.org/sites/default/files/members_area/medias/pdf/Technotes/TN65_Specific%20Fan%20Power.pdf> [retrieved on 20210329] *

Also Published As

Publication number Publication date
EP3404268A1 (de) 2018-11-21
CN207050304U (zh) 2018-02-27
ES2942180T3 (es) 2023-05-30
DK3404268T3 (da) 2023-04-03
DE102017111001A1 (de) 2018-11-22
US20180335244A1 (en) 2018-11-22

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