EP0040529A2 - Regeleinrichtung für die Luftklimatisierung - Google Patents

Regeleinrichtung für die Luftklimatisierung Download PDF

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Publication number
EP0040529A2
EP0040529A2 EP81302179A EP81302179A EP0040529A2 EP 0040529 A2 EP0040529 A2 EP 0040529A2 EP 81302179 A EP81302179 A EP 81302179A EP 81302179 A EP81302179 A EP 81302179A EP 0040529 A2 EP0040529 A2 EP 0040529A2
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EP
European Patent Office
Prior art keywords
air
heat
temperature
control
heat pump
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
Application number
EP81302179A
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English (en)
French (fr)
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EP0040529B1 (de
EP0040529A3 (en
Inventor
Alan Michael Turbard
Peter Neville Foley
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.)
BorgWarner Ltd
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BorgWarner Ltd
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Publication date
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Application filed by BorgWarner Ltd filed Critical BorgWarner Ltd
Priority to AT81302179T priority Critical patent/ATE11696T1/de
Publication of EP0040529A2 publication Critical patent/EP0040529A2/de
Publication of EP0040529A3 publication Critical patent/EP0040529A3/en
Application granted granted Critical
Publication of EP0040529B1 publication Critical patent/EP0040529B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0071—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater adapted for use in covered swimming pools
    • 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
    • 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
    • F24F11/32—Responding to malfunctions or emergencies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/001—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems in which the air treatment in the central station takes place by means of a heat-pump or by means of a reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature

Definitions

  • the present invention relates to an environmental control system, in particular to a system for controlling the environment in a closed space through which conditioning air is circulated.
  • the present invention provides an environmental control system to control the condition of a space including: air conditioning means; and means for delivering air to the space via the air conditioning means, characterised in that said delivery means comprises means for monitoring the enthalpies of air from said space and outside air and for selectively delivering whichever of the two has the higher enthalpy when heating of the air in said space is required.
  • the enthalpy of the air leaving the recirculating conduit and entering the closed space is at an optimum for the purpose required (namely either cooling the closed space or warming the closed space), and consequently the energy transfer required in order to bring the air to its desired final conditions is reduced.
  • the selection of the source of the air for the return circuit can be by way of controlled, variable incidence vanes.
  • the environmental control system in accordance with the present invention is designed as a control system for the air within a swimming pool hall 1.
  • a swimming pool hall represents just one application of the environmental control system of the present invention, and provides an advantageous heat store in the form of the mass of water in the pool.
  • Air is introduced to the pool hall by way of an inlet end 2 of the air recirculation conduit 3 and extracted via fan 9, passes through an outlet 4 to the various elements of the air conditioning means which are effective to ensure that the temperature and humidity of the air arriving at the inlet 2 at the downstream end of the recirculation conduit 3 are as desired.
  • the extracted air first passes through a filter 5 and then through a heat-exchanger 6 of a water "run around circuit” into which heat exchange cool water is separately pumped by way of a pump 7, so as to extract heat from the air as it leaves the filter 5.
  • the movement of the air is to a distribution region from which the air either leaves by way of an atmospheric vent 10, after passing through dampers 11, or passes on through a further damper 12 to recirculate to the pool hall.
  • damper 12 Just downstream of damper 12 is a fresh air inlet 13 through which air may be admitted into the recirculation air conduit 3, under the control of a third damper vane 14.
  • the air (which will usually be a mixture of partly recirculated air and partly ambient fresh air) passes through a further filter 15 and on to a second heat-exchanger 16 linked to the first-mentioned heat-exchanger 6 and the pump 7 to complete the simple "run around circuit" using water as the heat exchange medium.
  • Movement of the air from the second heat-exchanger 16 is fan-assisted by means of a second fan 17 as it embarks on its passage towards a condenser 18 of the heat pump system.
  • the air leaving the heat pump condenser 18 is passed through a third heat-exchanger 19, which may be heated by either low pressure hot water or steam from hot fluid circulation system 20. Finally, the air leaves the recirculation conduit at the inlet 2 to the pool hall.
  • the water "run around circuit" comprising the first and second heat-exchangers 6 and 16 and the pump 7 is brought into operation simply by energising the electric pump 7 upon the instructions of a control unit (not shown). This then serves to extract heat from the air leaving the filter 5 and to impart heat to the air leaving the filter 15 on. its way back to the pool hall inlet 2.
  • the heat pump system comprises not only the cooler 8 and the condenser 18, but also a four-stage single speed compressor 23, a desuperheater 24, and the condenser receiver 22.
  • the heat pump system comprises two parallel circuits, the first involving direct return of the refrigerant from the-desuperheater 24, by way of a shut-off valve B in a first refrigerant line 25, directly to the condenser/receiver 22.
  • the second circuit comprises both a second refrigerant line 26 to the heater 18 and a third refrigerant line 27 from the heater 18 back to the condenser/receiver 22, the second and third lines 26 and 27 being linked by multiple parallel paths through the heater.
  • the condenser 18 is a four-stage heater comprising a first stage 18a which is always in circuit between the second and third refrigerant lines 26 and 27 from the desuperheater 24 to the condenser receiver 22. Downstream of the first stage 18a is a one-way refrigerant flow control valve 28a.
  • the condenser 18 further comprises three additional parallel stages 18b, 18c, and 18dto which refrigerant is introduced by way of a common valve A and from which it is extracted by way of three branch lines connected to a refrigerant outlet manifold 27a in which a further one-way refrigerant flow control valve 28b is situated.
  • the cooler 8 is similarly a four stage parallel device, with individual control valve 29a, 29b, 29c and 29d to switch the respective parallel stages on line individually to select any number of operative stages from one stage to four stages.
  • Each of these valves 29a to 29d is controlled by a common control unit which in turn governs the operation of the valves A and B.
  • the four throttle valves control the refrigerant feed to the evaporator and thus reduce the operating ' pressure.
  • the type of valve fitted to this system is a thermostatic expansion valve.
  • the component S is a crankcase pressure regulator - used to protect the compressor against too high suction pressures.
  • the compressor 23 is a four-stage reciprocating compressor with the stages switchable so that for each of the four stages of the cooler 8 there will be a respective stage of the compressor 23 on line. In this way, the speed of operation of the compressor motor can be maintained constant and the pumping rate carefully matched to the throughflow capacity of the variable switchable cooler 8.
  • the desuperheater 24 in the heat pump system comprises a straightforward heat-exchanger to desuperheat the refrigerant leaving the compressor.
  • the heat rejected may be used to heat a limited quantity of hot water for use, for example, directly or indirectly for shower water purposes.
  • the three dampers 11, 12 and 14 are controlled so as to select the desired ratio of recirculated air.
  • the dampers themselves are controlled by a control unit which may comprise a particular control loop of the main control unit of the heat pump system, and is responsive to the enthalpy values determined by means of the recirculated air enthalpy-sensing temperature/ humidity sensor THl and the fresh air enthalpy-sensing temperature/humidity sensor TH2.
  • the dampers When the pool air dry bulb temperature determined by temperature/humidity sensor TH3 is below the set point, the dampers are adjusted so that the air to be delivered to the pool hall is from whichever source, i.e. the outside or the upstream part of the recirculation, has air of the higher enthalpy, whereas when the dry bulb temperature of the air in the pool hall is above the set point, the dampers will select air from the one of the two sources having the lower enthalpy.
  • the operation of the vanes of the damper 12 on the one hand and those of the dampers 11 and 14, on the other, is controlled in a modulated manner in response to the magnitude of the difference between the enthalpy values detected by sensors TH1 and TH2.
  • the heater comprising the hot fluid circuit 20 and the third heat-exchanger 19 includes a pump 30 and a boiler (not shown) providing the source of hot fluid.
  • a three-way variable control valve 31 is operated in a modulated manner so as to select, as a proportion of the total flow rate of pumped fluid in the circuit 20, the amount of that fluid which passes directly from the pump 30 to the valve 31 by way of a recycle line 32, the rest of the pumped fluid coming from the boiler by way of a line 33.
  • the valve 31 can be modulated between a fully opened position in which the recycle line 32 is effectively blanked off, and a fully closed position in which the supply line 33 from the boiler is fully closed.
  • the condenser receiver 22 in the heat pump system has a pool water circulation circuit 34 by way of a three-way modulatable control valve WRl. Water is pumped around the circuit 34 by means of the pump 35 such that it leaves the condenser receiver 22 and is then passed along a conduit 36 to a tee where one line 37 passes direct to the valve WRl and the other line 38 passes to the pool. Water is extracted from the pool by way of a further line 39, back to the valve WRl.
  • the valve WR1 is controlled in response to the condenser receiver pressure detected by the pressure sensor 21.
  • the intention is that this pressure 21 should be at an optimum value and thus, when the pressure 21 rises above its set point, the valve opens.
  • the valve WRl closes. In this way a steady state condition can be attained in which the proportion of the water pumped through the circuit 34 which has come from the pool by way of line 39 can be controlled due to the modulating operation of the valve WRl. In this way, heat extracted from the air in the recirculating conduit 3 (by means of the cooler 8) can be dumped into the pool water.
  • the heat pump system is controlled such that all stages of the cooler 8 are off and the compressor 23 is de-energised, to prevent further heat dumping, and so avoid too high an evaporation rate of the pool water which would create difficulties.
  • the initial recovery action involves bringing on line the heater comprising hot fluid control circuit 20 with its heat-exchanger 19. This is instead of initially bringing the heat pump system on line.. This is because, when operating on only its first stage, the efficiency of the heat pump is at its lowest and to restore the temperature to the set point from a small undertemperature value, it is.more economical of prime energy to use the prime energy to heat the air directly rather than to use it to operate the heat pump.
  • the water "run around circuit" comprising the first and second heat-exchanger 6 and 16 is in operation whenever the dry bulb temperature of the pool hall is below the set point, as this provides a relatively cheap means of effecting a measure of heat transfer between the warm air leaving the pool hall and the relatively cooler air on its way to the pool hall.
  • the hot fluid circuit 2 0 is switched off line, and the heat pump system progressively brought on line one stage at a time. Only when the temperature continues to fall despite'all four stages of the heat pump system being on line does the hot fluid circuit 20 come back on line in order to prompt temperature recovery.
  • the pump 7 of the water "run around circuit” is immediately energised to start operation.
  • the pump 30 of the low pressure hot water (LPHW) circuit 20 (previously referred to more generally as a “hot fluid circuit”) is energised and the three-way valve 31 is initially set to its position in which the boiler line 33 is closed off and the return line 32 is open.
  • the compressor 23 is de-energised but the valve A is closed and the valve B is open so that the heat pump system is standing by to come on line shortly with one stage of cooler 8 and a single stage 18a of condensor 18.
  • the valve 31 will have been modulated to its position in which the return line 32 is closed off and the boiler line 33 is fully open, but this will have been ineffective to restore rapidly the dry bulb temperature measured by the sensor TH3.
  • the LPHW pump 30 is de-energised and the first stage of the cooler 8 is brought on line by opening of the valve 29a and energising of the compressor 23 with one compressor stage effective.
  • valves A and B At a second threshold temperature, in this case 26.25°C, the conditions of the valves A and B reverse so that valve B closes and valve A opens to bring the last three stages.18b, 18c and 18d of the condensor 18 of the heat pump system on line simultaneously with no refrigerant returning directly from the desuperheater 24 to the condenser/receiver 22 (because the valve B is closed). However, at this point only one stage of the cooler 8 and one compressor stage are on line.
  • a third threshold temperature in this case 26°C the second stage of the cooler 8 is brought on line by opening of the valve 29b, and simultaneously a second stage of the compressor 23 is effective.
  • the third stage of the cooler 8 is brought on line by opening of the valve 29c, and a third stage of the compressor 23 is brought on line.
  • the fourth stage of the cooler is brought on line by opening of the valve 29d and the fourth stage of the compressor 23 is also brought on line.
  • the heater circuit pump 30 is energised, but again with the three-way valve 31 in its position closing off the boiler line 33 and leaving the return line 32 fully open.
  • valve 31 in the low pressure hot water circuit progressively modulates to its alternative extreme position where the return line 32 is closed and the boiler line 33 is fully open, by the time a sixth threshold temperature, in this case 24°C, is reached.
  • a sixth threshold temperature in this case 24°C
  • valve.31 progressively modulates back to its position in which the return line 32 is fully open and the boiler line 33 is fully closed by the time the temperature of 24.5.°C has been attained; the pump 30 remains in operation until the temperature has recovered to 25°C. At this point all four stages of the cooler 8 and of the compressor will still be in operation.
  • the fourth stage of the heat pump system is brought off line by a closing valve 29d and bringing one of the four compressor stages off line.
  • the third heat pump stage is brought off line by closing down another stage of the compressor (leaving only two compressor stages in operation) and by closing valve 29c.
  • the temperature decrements required to bring the first and second stages into operation may be smaller (say 0.5°C) than the decrements required to bring in the third and fourth stages (say, 1°C); this would ensure that with falling temperature, the number of stages of the compressor which were operating would increase more rapidly - this could be important as the coefficient of performance increases as more stages of the compressor are brought into operation.
  • the heat pump first stage is switched on (with the valves A and B still in the "A closed -B open” configuration) so that one stage of the cooler 8 and one stage 18a of the heater will be operating and the system dumping heat to the pool water.
  • the vanes 12 are closed slightly and the vanes 11 and 14 are opened slightly so as to increase the fresh air intake in an attempt to depress the dry bulb temperature or in any event to reduce the humidity levels.
  • the fresh air dampers 11 and 14 will be fully open and the recirculating air damper l2 fully closed by the time the temperature is 28.5°C, with the heat pump first stage still in operation.
  • the heat pump first stage will be switched off in order to prevent further heat from being dumped to the pool water by way of the condenser receiver 22 and the pool water circuit 34.
  • the humidity control facility is of course interlocked with the dry bulb control such that in the event of an increase in humidity, the following sequence will occur:
  • valve A opens and the valve B closes so as to bring the remaining three stages 18b, 18c and 18d of the heater on line.
  • the second stage of the cooler is brought on line by opening of valve 29b and at the same time bringing a second stage of the compressor 23 on line.
  • a further increase in humidity leads firstly to bringing of the third cooler stage on line, and then finally to bringing the fourth cooler stage on line. As the relative humidity falls, the control sequence is the reverse.
  • a selector module of the control unit will determine which of these signals is the higher and will energise the heat pump accordingly.
  • the window sensor Wl is used to reset the set point of the humidity controller automatically in response to a change in the glass surface temperature, so as to ensure that at all times the humidity detected by the temperature/humidity sensor-TH3 is such that the dew point of the air in the pool hall is just less than the glass surface temperature, thereby avoiding the formation of condensation on the windows.
  • the window sensor will then open the dampers 11 and 14, with corresponding slight closing of the damper 12, in order to increase the fresh air intake and thereby, hopefully, to depress the dew point temperature.
  • the maintenance of design operating efficiency of the heat pump system requires limiting of the refrigerant condensing pressure.
  • This is achieved by way of the pressure sensor 21 which controls the three-way valve WRl of the pool water circuit in such a way that if condensing pressure in the condenser/receiver 22 rises above its set point the valve WRl modulates open to bring more of the water in the line 34 from the pool line 39, whereas a fall in pressure detected by the sensor 21 will modulate the valve WRl closed so as to reduce the amount of the water in line 34 coming from line 39 and to bring a higher proportion straight from the condenser/receiver by way of the line 37.
  • the pressure control is totally independent of both the dry bulb and humidity controllers, but of course will interact with those control modes by virtue of its effect of changing the origin of the pool water in the condenser/receiver 22.
  • the enthalpy comparison controller simply uses the temperature/humidity sensors THl and TH2 to determine the best source of air, i.e. recirculated air or fresh air, in order to ensure that the minimum energy transfer, and hence the minimum energy consumption, is needed under any particular mode of operation.
  • the comparison of enthalpy is a continuous function and overrides other considerations determining the settings of dampers 11, 12 and 14. It was indicated above, with reference to the dry bulb temperature controlling mode, that the dampers bring in more fresh air if the dry bulb temperature exceeds the set point. It is this aspect of the damper control which may be overridden by the enthalpy comparison control circuit.
  • the enthalpy comparison control is reverse- acting in that when the system is operating in the heating mode the sensors TH1 and TH2 will select the air mixture (recirculating air or fresh air or combination of the two) which has the highest enthalpy, whereas in the cooling mode the air mixture with the lowest enthalpy will be selected.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Central Air Conditioning (AREA)
  • Air Conditioning Control Device (AREA)
  • Selective Calling Equipment (AREA)
  • Road Signs Or Road Markings (AREA)
  • Gas-Insulated Switchgears (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
EP81302179A 1980-05-19 1981-05-15 Regeleinrichtung für die Luftklimatisierung Expired EP0040529B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81302179T ATE11696T1 (de) 1980-05-19 1981-05-15 Regeleinrichtung fuer die luftklimatisierung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8016457 1980-05-19
GB8016457 1980-05-19

Publications (3)

Publication Number Publication Date
EP0040529A2 true EP0040529A2 (de) 1981-11-25
EP0040529A3 EP0040529A3 (en) 1982-01-20
EP0040529B1 EP0040529B1 (de) 1985-02-06

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ID=10513508

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81302179A Expired EP0040529B1 (de) 1980-05-19 1981-05-15 Regeleinrichtung für die Luftklimatisierung

Country Status (4)

Country Link
EP (1) EP0040529B1 (de)
AT (1) ATE11696T1 (de)
DE (1) DE3168741D1 (de)
ES (1) ES502268A0 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0269399A2 (de) * 1986-11-24 1988-06-01 Allan Dr. Shaw Klimagerät und Verfahren zur Regelung der Entfeuchtung
US5461877A (en) * 1991-05-24 1995-10-31 Luminis Pty Ltd. Air conditioning for humid climates
WO2007095984A1 (de) 2006-02-17 2007-08-30 Menerga Apparatebau Gmbh Anlage zum erwärmen einer einrichtung wie einer halle mit hohem temperaturniveau die entfeuchtet werden muss, insbesondere einer schwimmhalle
EP1857744A2 (de) * 2006-05-16 2007-11-21 J. D. Schwimmbad-Bau + Design GmbH Verfahren und Vorrichtung zur Regelung der Luftfeuchtigkeit
WO2011079371A1 (en) * 2010-01-04 2011-07-07 Andre Boucher An air conditioning system including a desuperheater
CN102155773A (zh) * 2011-05-12 2011-08-17 宁波工程学院 一种热回收式热泵空调***
CN102418966A (zh) * 2011-12-19 2012-04-18 东南大学 一种空气处理装置及空气处理方法
CN104456732A (zh) * 2014-11-27 2015-03-25 广东芬尼克兹节能设备有限公司 多功能浴室设备
CN106766026A (zh) * 2016-12-30 2017-05-31 江苏天舒电器股份有限公司 一种变风量泳池变频除湿兼池水恒温***及其运行模式
CN107101286A (zh) * 2017-06-01 2017-08-29 广东申菱环境***股份有限公司 一种蒸发冷却除湿空调机组及其控制方法
CN112254195A (zh) * 2020-10-21 2021-01-22 程东东 一种利用新能源加热的浴场保温机
CN114857680A (zh) * 2022-03-11 2022-08-05 上岛(浙江)环境科技有限公司 一种调温除湿机

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JP2016171840A (ja) * 2015-03-16 2016-09-29 パナソニックＩｐマネジメント株式会社 環境制御システム、制御装置、プログラム

Citations (7)

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Publication number Priority date Publication date Assignee Title
DE2165531A1 (de) * 1971-12-30 1973-07-05 Witte Haustechnik Gmbh Anlage zur entfeuchtung und klimatisierung von hallenschwimmbaedern oder dergl
US3844338A (en) * 1970-12-01 1974-10-29 H Hilgemann Method of operating public bath and the like
DE2402347A1 (de) * 1974-01-18 1975-07-24 Buderus Eisenwerk Anlage zum entfeuchten und beheizen der luft eines hallenbades
DE2413618A1 (de) * 1974-03-21 1975-09-25 Happel Kg Vorrichtung zum entfeuchten und temperieren der raumluft in schwimmbaedern, insbesondere bei einem swimmingpool
DE2417082A1 (de) * 1974-04-08 1975-10-16 Pflueger Apparatebau Gmbh & Co Energiesparende versorgungsanlage zur klimatisierung und beheizung von hallenbaedern
US3913344A (en) * 1974-10-15 1975-10-21 Johnson Service Co Fluid energy monitoring apparatus
FR2394027A1 (fr) * 1977-06-09 1979-01-05 Missenard Quint Ets Deshumidification d'un local de piscine couverte par un systeme frigorifique a detente directe deshydratant l'air de reprise, rejetant les calories dans l'eau et dans l'ambiance, avec volet, pour pompe a chaleur lors de l'ouverture du local

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3844338A (en) * 1970-12-01 1974-10-29 H Hilgemann Method of operating public bath and the like
DE2165531A1 (de) * 1971-12-30 1973-07-05 Witte Haustechnik Gmbh Anlage zur entfeuchtung und klimatisierung von hallenschwimmbaedern oder dergl
DE2402347A1 (de) * 1974-01-18 1975-07-24 Buderus Eisenwerk Anlage zum entfeuchten und beheizen der luft eines hallenbades
DE2413618A1 (de) * 1974-03-21 1975-09-25 Happel Kg Vorrichtung zum entfeuchten und temperieren der raumluft in schwimmbaedern, insbesondere bei einem swimmingpool
DE2417082A1 (de) * 1974-04-08 1975-10-16 Pflueger Apparatebau Gmbh & Co Energiesparende versorgungsanlage zur klimatisierung und beheizung von hallenbaedern
US3913344A (en) * 1974-10-15 1975-10-21 Johnson Service Co Fluid energy monitoring apparatus
FR2394027A1 (fr) * 1977-06-09 1979-01-05 Missenard Quint Ets Deshumidification d'un local de piscine couverte par un systeme frigorifique a detente directe deshydratant l'air de reprise, rejetant les calories dans l'eau et dans l'ambiance, avec volet, pour pompe a chaleur lors de l'ouverture du local

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0269399A3 (en) * 1986-11-24 1989-07-26 Allan Dr. Shaw Air conditioner and method of dehumidifier control
EP0269399A2 (de) * 1986-11-24 1988-06-01 Allan Dr. Shaw Klimagerät und Verfahren zur Regelung der Entfeuchtung
US5461877A (en) * 1991-05-24 1995-10-31 Luminis Pty Ltd. Air conditioning for humid climates
DE102006007848B4 (de) 2006-02-17 2022-03-17 Menerga Gmbh Anlage zum Erwärmen einer Einrichtung wie einer Halle mit hohem Temperaturniveau, die entfeuchtet werden muss, insbesondere einer Schwimmhalle
WO2007095984A1 (de) 2006-02-17 2007-08-30 Menerga Apparatebau Gmbh Anlage zum erwärmen einer einrichtung wie einer halle mit hohem temperaturniveau die entfeuchtet werden muss, insbesondere einer schwimmhalle
EP1857744A2 (de) * 2006-05-16 2007-11-21 J. D. Schwimmbad-Bau + Design GmbH Verfahren und Vorrichtung zur Regelung der Luftfeuchtigkeit
EP1857744A3 (de) * 2006-05-16 2010-11-03 J. D. Schwimmbad-Bau + Design GmbH Verfahren und Vorrichtung zur Regelung der Luftfeuchtigkeit
WO2011079371A1 (en) * 2010-01-04 2011-07-07 Andre Boucher An air conditioning system including a desuperheater
CN102155773A (zh) * 2011-05-12 2011-08-17 宁波工程学院 一种热回收式热泵空调***
CN102418966A (zh) * 2011-12-19 2012-04-18 东南大学 一种空气处理装置及空气处理方法
CN104456732B (zh) * 2014-11-27 2017-09-19 广东芬尼克兹节能设备有限公司 多功能浴室设备
CN104456732A (zh) * 2014-11-27 2015-03-25 广东芬尼克兹节能设备有限公司 多功能浴室设备
CN106766026A (zh) * 2016-12-30 2017-05-31 江苏天舒电器股份有限公司 一种变风量泳池变频除湿兼池水恒温***及其运行模式
CN107101286A (zh) * 2017-06-01 2017-08-29 广东申菱环境***股份有限公司 一种蒸发冷却除湿空调机组及其控制方法
CN107101286B (zh) * 2017-06-01 2022-09-30 广东申菱环境***股份有限公司 一种蒸发冷却除湿空调机组及其控制方法
CN112254195A (zh) * 2020-10-21 2021-01-22 程东东 一种利用新能源加热的浴场保温机
CN114857680A (zh) * 2022-03-11 2022-08-05 上岛(浙江)环境科技有限公司 一种调温除湿机

Also Published As

Publication number Publication date
ES8204136A1 (es) 1982-04-01
EP0040529B1 (de) 1985-02-06
ATE11696T1 (de) 1985-02-15
ES502268A0 (es) 1982-04-01
EP0040529A3 (en) 1982-01-20
DE3168741D1 (en) 1985-03-21

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