CN101000163A - Dehumidifying air conditioning system - Google Patents

Dehumidifying air conditioning system Download PDF

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Publication number
CN101000163A
CN101000163A CNA2007100016955A CN200710001695A CN101000163A CN 101000163 A CN101000163 A CN 101000163A CN A2007100016955 A CNA2007100016955 A CN A2007100016955A CN 200710001695 A CN200710001695 A CN 200710001695A CN 101000163 A CN101000163 A CN 101000163A
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CN
China
Prior art keywords
air
heat
dehumidifier
conditioning
heat pump
Prior art date
Application number
CNA2007100016955A
Other languages
Chinese (zh)
Inventor
藤居达郎
今成正雄
高桥稔
杉浦匠
头岛康博
福井伊津志
Original Assignee
株式会社日立工业设备技术
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to JP2006005474 priority Critical
Priority to JP2006005474A priority patent/JP4591355B2/en
Priority to JP2006159201 priority
Application filed by 株式会社日立工业设备技术 filed Critical 株式会社日立工业设备技术
Publication of CN101000163A publication Critical patent/CN101000163A/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00Devices or apparatus used for air treatment
    • F24F2203/10Rotary wheel
    • F24F2203/1032Desiccant wheel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00Devices or apparatus used for air treatment
    • F24F2203/10Rotary wheel
    • F24F2203/1056Rotary wheel comprising a reheater
    • F24F2203/106Electrical reheater
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00Devices or apparatus used for air treatment
    • F24F2203/10Rotary wheel
    • F24F2203/1068Rotary wheel comprising one rotor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00Devices or apparatus used for air treatment
    • F24F2203/10Rotary wheel
    • F24F2203/1088Rotary wheel comprising three flow rotor segments
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2309/00Gas cycle refrigeration machines
    • F25B2309/06Compression machines, plant or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061Compression machines, plant or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure

Abstract

In a dehumidifying system using a desiccant dehumidifier, regeneration air at the desiccant dehumidifier is heated by the condenser of a heat pump or a gas cooler, indoor return air re-circulated from an air-conditioned indoor to a dehumidifying rotor is cooled by an evaporator. Since the cooling load of indoor return air is almost stable during operations, the size of a heat pump unit is made small as compared with outdoor air cooling by setting the capacity of the heat pump to match this cooling load to thereby reduce initial costs. Furthermore, the heat pump can be operated at an almost maximum capacity throughout operating periods to provide a stabilized energy saving effect.

Description

Dehumidifier/air-conditioning system

Technical field

The present invention relates to a kind of dehumidifier/air-conditioning system, it serves as basic with the drier air conditioner, and as he the air heat cooling body and have heat pump.

Background technology

As dehumidifier/air-conditioning system involved in the present invention, can enumerate for example special technology of being put down in writing in the 2005-34838 communique of opening.In this communique, become following structure: have the cooling medium loop promptly as the desiccant rotor of heat pump and moisture adsorption and releasing mechanism, radiator by described heat pump heats dehumidifying object air, humidification is carried out to this air in moisture releasing zone in described desiccant rotor, utilize the heat dump of described heat pump that this air is cooled off, and in the dilution zone of desiccant rotor, dehumidify.In addition, in this known example, the cooling medium of heat pump carries out heat release with supercritical pressure in radiator, and uses carbon dioxide for cooling medium.

In addition, as the background technology of employed heat pump cycle cooling among relevant the present invention, can exemplify out the spy open flat 7-18602 communique and NEDO put down into 13 annual inquiry report 51401011-0-1 carbon dioxide cooling mediums etc. applied for machines research p.105.In these documents, disclose that the low pressure cooling medium utilizes the heat of high pressure cooling medium and the additivity heater that evaporated or heat is promptly sought the supercritical steam compression cycle that ability increases by inner heat exchanger is set.

In addition, have the spy as dehumidifier/air-conditioning system and open disclosed system in the 2005-201624 communique.In this communique, by constituting dehydrating unit for gas circuit, exhaust line, sorbing material maintaining body and heat pump, and be disposed at more close upstream side in gas circuit and the exhaust line low-temperature heat source and high temperature heat source with heat pump at each.So,, can seek energy and save by low-temperature heat source and the high temperature heat source that effectively utilizes this heat pump.

In addition, as other conventional arts involved in the present invention, in putting down into 17 annual air mediation/health engineerings meeting conference lecture collection of thesis pp.1233-1236 Fig. 1, enumerate known technology.In this known example, seeking to save energy by means of the importing of heat pump when, as the regeneration air of dehumidifying rotor with and auxiliary heater is set, and after the high temperature heat source by heat pump heats regeneration air, further heat by this auxiliary heater, and the guiding dehumidifying rotor regeneration zone and constitute.

Opening in the conventional art of 2005-34838 communique above-mentioned spy, is object with employed dehydrating unit in the general air-conditioning, gas outside therefore using in the regeneration usefulness air by the heat pump heating.Yet, under the situation that needs low humidity, low dew point environment, use is provided with the so-called cleaning-type drier dehumidifier that cleans the zone on dryer rotor, at this moment, used in the air by the regeneration of heat pump, the cleaning that is used for rotor is cooled air, the outer temperature Du Genggao of this air ratio, therefore exist heat release to become insufficient, and cooling COP reduce the problem that consumed power increases from heat pump.

In addition, open in the conventional art of 2005-34838 communique above-mentioned spy, the air heat that the heat unit of use heat pump will be taken in from the outside, and carry out the regeneration of desiccant rotor, but owing to the consideration of not carrying out at the change of outer gas condition, therefore regeneration temperature and accompany therewith to the air humidity degree with having bigger change season, and the distribution that adds heat and cooling heat is determined by heat pump cycle that also existence is difficult to the problem corresponding with outer gas phase.In addition, owing to only regenerate with the heating of air the problem that therefore exist the upper limit of regeneration air temperature lower, dehumidifying effect also is restricted to this with the heat unit of heat pump.

In addition, open in the conventional art of 2005-34838 communique above-mentioned spy, though suppose to use in the cooling medium of heat pump the less carbon dioxide of greenhouse effects of the earth coefficient, and carry out the heating of regeneration air with supercritical pressure, but under the situation of the high temperature heating of the usefulness of regenerating in that carbon dioxide is used for the cooling medium of heat pump air, in order to obtain high temperature, and need be with cooling medium boil down to high pressure in compressor, because of the adiabatic efficiency of compressor and volume efficiency reduce the problem that the capacity that causes consumed energy and heat pump assembly increases, in above-mentioned conventional art, do not make consideration at this problem points.

In addition, above-mentioned NEDO puts down in the conventional art of 13 annual inquiry report 51401011-0-1, owing to the reduction of compression ratio makes the raising and the catabiotic reduction of the adiabatic efficiency that possesses compressor, and played bigger effect with the setting of inner heat exchanger accordingly of this effect, do not mention for this point.

In addition, open in the conventional art of 2005-201624 communique the spy, by identical freeze cycle, carry out being taken into to the supply in gas circuit footpath and give the cooling of gas, and be intended to and be used for the heating of the regeneration of adsorbent from the indoor discharge air (regeneration air) that is taken into exhaust pathway from outside such as outdoor.Yet, supply with to give the cooling heat of gas, because of the time fluctuation and the seasonal move of outer temperature degree changes significantly.For this reason, there are the following problems: promptly in a single day make the heat pump cycle action accordingly with this variation, then the heat that adds of evacuating air also changes, thereby the reproduced state of adsorbent, and then is also changed by the air fed wet-out property that this adsorbent carried out.In addition, such as described above, the operating condition of heat pump is with the change significantly corresponding to the cooling load of outer gas condition, and the term restriction of heat-pump apparatus effective action is in the bigger state of cooling load, and existence runs through its energy-saving effect problem of smaller all the time between on-stream period.

In addition, for the situation that auxiliary heaters such as electricity is set for the change that adds heat to the discharge air compensates heat the discharge air again, existence makes the auxiliary heater load increase and then consume the problem of energy increase because of the change of the operating condition of heat pump.

For these problems, can conference give a lecture in the collection of thesis in the above-mentioned 17 annual air mediation health engineerings of putting down into, after the high temperature heat source with heat pump heats regeneration air, utilize assisted heat pump and further heat, can make the temperature stabilization of the regeneration air that supplies to regeneration zone thus, and the reproduced state of adsorbent and air fed wet-out property are stablized.

In addition, change for cooling load, setting makes from indoor discharge air with by dehumidifying rotor and is dehumidified and temperature rises to sensible heat (sensible Hot) rotor of about 65 ℃ air supply heat exchange, the structure of air supply carry out heat exchange with room air in this sensible heat rotor after being cooled off by means of the low-temperature heat source that uses heat pump, and suppress the influence of extraneous gas change, and it doesn't matter that ground makes the heat-pump apparatus action effectively with the time fluctuation of outer gas condition and seasonal move.But, in this conventional art, because the sensible heat rotor is necessary, so the problem that exists dehumidification system comparatively to maximize.

Summary of the invention

The objective of the invention is to, in using the drier dehumidifier of heat pump, with the change of outer gas condition irrespectively, supplies with stable low humidity air, make the heat pump operating stably simultaneously and seek the saving of energy and the maximization of inhibition dehumidification system device.Another object of the present invention is to, under the situation that will be the heating and cooling that are used for air of heat pump that cooling medium cooling medium, heat unit is a supercritical pressure with carbon dioxide etc., reduce the pressure cooling medium in the compressor outlet, reduced compression ratio and improved the adiabatic efficiency of compressor, reduced the consumption electric power of dehumidified air system.

In order to achieve the above object, in the dehumidifier/air-conditioning system involved in the present invention, use the heating of regeneration air and the chiller-heat pump of supply, and in this heat pump cycle side, except the radiator of heating of regeneration air is carried out in setting, the heat release mechanism of on high-tension side cooling medium being cooled off by means of the external refrigeration medium is set also.

In addition, handling that air is considered as the outer gas that imports from the outside and, and return in recirculation indoor and be provided with on the stream of gas the endothermic section of heat pump aerial cooler as cooling source from the indoor mixing air that returns gas of indoor importing of air-conditioning object and recirculation.

According to above-mentioned dehumidifier/air-conditioning system, owing to using heat pump to carry out the heating of regeneration air, therefore situation about heating with respect to only using electric heater consumes the electric power minimizing, by means of heat release mechanism to the outside, the cooling effectiveness of heat pump is improved, thereby can further reduce consumption electric power.In addition, owing to carry out the cooling of room air by the endothermic section of heat pump, therefore, start under the situation of dehumidification air conditioner at the production scene that throughout the year produces the office of cooling load, workshop, cooling chamber etc., can obtain roughly stable cooling load throughout the year, the result can start heat-pump apparatus effectively, and can access the energy-saving effect of corresponding its ability.

Description of drawings

Fig. 1 is the overall system view of the related dehumidifier/air-conditioning system of one embodiment of the present of invention.

Fig. 2 is the T-h line chart of the heat pump cycle among the embodiment of Fig. 1.

Fig. 3 is the curve map of the consumption energy in the dehumidifier/air-conditioning system of presentation graphs 1.

Fig. 4 is all system diagrams of the related dehumidifier/air-conditioning system of other embodiment of the present invention.

Fig. 5 is the T-h line chart of the heat pump cycle among the embodiment of Fig. 4.

Fig. 6 is with the relation of the temperature efficiency of inner heat exchanger and the curve map of the compression ratio of the consumption electric power of the dehumidifier/air-conditioning system among the embodiment of presentation graphs 4 and compressor.

Fig. 7 is the catabiotic curve map of the dehumidifier/air-conditioning system among the embodiment of presentation graphs 4.

Fig. 8 is the overall system view of the related dehumidifier/air-conditioning system of expression other embodiment of the present invention.

Fig. 9 is the T-h curve map of the heat pump cycle among the embodiment of presentation graphs 8.

Figure 10 is the figure of the cellular construction among the embodiment of presentation graphs 8.

Figure 11 is the curve map of the consumption electric power of the dehumidifier/air-conditioning system among the embodiment of presentation graphs 8.

Figure 12 be the dehumidifier/air-conditioning system among the embodiment of presentation graphs 8 consumption electric power in the period of the curve map of change.

Figure 13 is the overall system view of the related dehumidifier/air-conditioning system of other embodiment of the present invention.

Embodiment

Use Fig. 1, Fig. 2 and Fig. 3 that embodiment 1 is described.Fig. 1 is the overall system view of the related dehumidifier/air-conditioning system of present embodiment.Fig. 2 is the figure that represents employed heat pump cycle in the present embodiment on temperature-heat content line chart.Fig. 3 is the consumed energy of dehumidifier/air-conditioning system that present embodiment is related and the curve map that detailed and similar system compares thereof.

As shown in Figure 1, dehumidifier/air-conditioning system is by constituting as lower member: promptly desiccant rotor (after, be called dehumidifying rotor) 10, heat pump 30, electric heater 70, refrigerator 80, and make the conduit of handling air and desiccant regeneration air draught and fan etc. in these.

Dehumidifying rotor 10, by rotation in turn and to dehumidifying as lower area: promptly to the wet branch of handling air adsorb the processing region 11 that dehumidifies, the regeneration air that utilizes high temperature will wet the regeneration zone 12 that branchs remove from rotor, the cleaning zone 13 of the rotor that the temperature rising has taken place being cooled off by handling the part of air shunt regeneration zone.In addition, in dehumidifying rotor 10, keep dehumidifying members such as silica gel and zeolite.

Heat pump 30 is made of following device: be about to that cooling medium gas is compressed to supercriticality and compressor 31 that temperature is risen; Utilization is become the cooling medium air heater 32 that regeneration is heated with air 95 to rotor of high temperature by compressor 31 boil down to supercritical pressures; The outer hot-air heater 33 that utilizes heat release further to cool off with 99 pairs of cooling mediums that temperature reduces in air heater 32 of outer gas; And the cooling medium that will flow out from outer gas radiator 33 is the pressure-reducing valve 34 of two phase regions from the supercriticality decompression; Aerial cooler 35,36, the evaporations of its cooling fluid such as cooling medium by becoming two-phase etc. are promptly cooled off from indoor also gas 94 of not shown low dew point and the outer gas that is imported handling air; And the cooling medium pipe arrangement 37 that connects above-mentioned member.

In addition,, be provided with at each position of conduit: temperature sensor 39, it is used to carry out the volume controlled of heat pump 30; Temperature sensor 79, it detects the temperature of rotor regeneration with air 95 for the control of carrying out electric heater 70; Temperature sensor 89, its running that stops for the starting that comprises refrigerator 80 control and to measuring by the temperature that is set in the outer gas 91 of importing behind the direct-expansion type cooling spiral pipe 81 on the refrigerator 80.That is to say, constitute by this refrigerator 80 and direct-expansion type cooling spiral pipe 81 and prepare the auxiliary cooling body of cooling importing outer gas (processing air).

Next, the basic action of the related dehumidifier/air-conditioning system of present embodiment is described.In dehumidifier/air-conditioning system, utilize initial 81 pairs of conducts of direct-expansion type cooling spiral pipe that on refrigerator 80, are provided with to prepare cooling for the outer gas 91 that imports from the outside with gas.In addition, prepare cooled outer gas by the cooling of the aerial cooler 36 of heat pump 30 after, collaborate from the indoor gas 94 cooled air that return of low dew point with 35 pairs of aerial coolers that utilizes heat pump 30.Air behind this interflow, a part is directed to cleaning zone 13 as scavenging air 92 along separate routes, after remainder is directed to processing region 11 and temperature is descended, as be directed to not shown low dew point chamber to gas.

On the other hand, scavenging air 92,13 pairs of dehumidifying rotors 10 cool off in the cleaning zone.Thus,, only being carried out to gas from sufficiently cooled zone by known mode as the feature of cleaning-type drier dehumidifier, the result can access the low-down gas of giving of temperature.Because of dehumidifying rotor 10 being cooled off the scavenging air 92 after temperature rises, become regeneration air with recirculation regeneration air 96 interflow, in addition, after being heated in turn by the air heater 32 of heat pump 30, electric heater 70, be directed to regeneration zone 12 and regenerate, promptly to removing from the moisture of dehumidifying rotor 10.

From the regeneration air 95 of regeneration zone 12, a part is collaborated as recirculation air 96 and washed air 92 along separate routes as described above, and remainder is removed moisture by dehumidifying rotor 10, and is discharged to outside the machine as exhaust 97.

Next, use Fig. 2 that the action of the heat pump 30 of this moment is described.In the present embodiment, as the working media use carbon dioxide of heat pump 30, the state of the cooling medium on the temperature-heat content line chart shown in the mark A~F presentation graphs 2 among Fig. 2 represents that curve (fine rule) H represents saturated line.

Be compressed to the cooling medium of critical pressure by compressor 31, temperature rises and becomes state A, and is directed to air heater 32.In air heater 32, coolant temperature descends and regeneration air 97 is heated and becomes state B, and is directed to outer gas radiator 33.In the gas radiator 33, the heat release that is imported into is lower than the regeneration air temperature that flow into air heater 32 with outer gas 99 outside, so coolant temperature descends and becomes state C.After this, cooling medium is directed to expansion valve 34 and reduces pressure, and the two-phase state that becomes by cooling medium liquid and cooling medium vapour composition is state D.In aerial cooler 35,36, the indoor outer gas 91 that returns gas 94, imports is cooled off respectively by cooling medium evaporation of liquid latent heat.In aerial cooler 36, all cooling medium liquid evaporation and become state E more than the saturated line, and become the state F of superheated steam by the heat exchange with outer gas 91 after is attracted and is compressed once more by compressor 31.

In addition, in fact in each heat exchanger, exist the pressure loss, but in Fig. 2, omit its influence and on the isobar of supercritical range, show state A, B, C.And on the isobar of the gentle body region in two-phase zone, show state D, E, F.

Next, the running control to the related dehumidifier/air-conditioning system of present embodiment describes.In the present embodiment, heat pump 30, in air heater 32 based on 95 maximum heat that can reclaim of regeneration air and the upper limit of setting ability and cooling medium internal circulating load.Therefore, can think cooling capacity deficiency under the situation that the temperature degree is high outside, for this defence is provided with refrigerator 80.Based on to by refrigerator the temperature of freezing outer gas carry out the temperature sensor 89 of instrumentation, and this refrigerator 80 is controlled.

Outside under the situation that the temperature degree is high, refrigerator 80 is controlled so that become roughly certain value by the air themperature of 89 instrumentations of temperature sensor.The value of this air themperature, corresponding to the cooling capacity of the heat pump 30 in following such operating condition and determine: promptly described heat pump 30 can supply with regeneration air 95 in air heater 32 the maximum heat that can reclaim.

Under the situation that the temperature degree is lower, it is less that cooling load becomes outside, and only the cooling capacity by heat pump 30 can fully satisfy outer gas 91 and the indoor cooling of returning gas 94, and therefore the running with refrigerator 80 stops.In addition, in this case,, therefore preferably the running of heat pump 30 is not stopped because of the heat that adds of air heater is zero to make the consumption electric power of electric heater 70 increase.In the present embodiment, if be lower than the value of regulation by the air themperature of 89 instrumentations of temperature sensor, then stop the running of refrigerator 80, surpass the value that on described setting, adds certain action gap (hysteresis) if this air themperature rises once more, then begin the running of refrigerator 80 once more.

Based on to by 35,36 of aerial coolers respectively the indoor gas 94 that returns of cooling carry out the output of the temperature sensor 39 of instrumentation with outer gas 91 mixed processing air themperatures, and heat pump 30 is controlled.At this moment, the indoor temperature of returning gas 94 in the inlet of aerial cooler 35 is an almost fixed, the temperature of the outer gas 91 in the inlet of aerial cooler 36 is maintained below the uniform temperature by refrigerator 80 as described above, therefore by the temperature of the processing air of 39 instrumentations of temperature sensor, in heat pump 30 volume controlled scopes, roughly be controlled as fixed value.In addition, this value is determined by the standard of supplying with to low dew point chamber from dehumidifier/air-conditioning system of giving gas.

Outside in the state that low, the refrigerator 80 of temperature degree stops because of aforementioned control action, as described above by heat pump 30 being carried out volume controlled and can being almost fixed with the temperature maintenance of mixing air, therefore accompany therewith, the air heat amount in the air heater 32 also changes.Corresponding with this variation, based on to the output of the temperature sensor 79 that detects to the temperature of the regeneration air of the regeneration zone 12 of dehumidifying rotor 10 from electric heater 70 and the heat that adds based on heat pump 70 is controlled, and be setting, thereby the dehumidifying effect in the processing region 11 is kept the temperature maintenance of regeneration air.

As described above, in the present embodiment, by the endothermic section with heat pump cycle is evaporimeter as the cooling source of handling air, and heat unit is used as the heating source of regeneration air, can seek catabiotic reduction by the effects such as load that reduce electric heater 70.In addition, by outer gas radiator 33 is set, cooling medium be carbon dioxide after the heat unit of heat pump cycle heats and becomes state B to regeneration air 95, heat release with outer gas 99 in further heat release and temperature is reduced to state C.That is to say that the heat content difference that the cooling capacity in the aerial cooler 35,36 becomes between state D-state F among Fig. 2 is QE.If this cooling capacity is compared with the situation of not using outer gas radiator 33, outside not using under the situation of gas radiator 33, cooling medium is depressurized and becomes state D ' from state B, and the heat content difference that cooling capacity becomes between state D '-state F is QE '.For this reason, by outer gas radiator 33 is set, the cooling capacity of per unit cooling medium consumption increases the amount of (QE-QE '), and the electric energy of putting into compressor 31 also reduces.Perhaps, by means of the recruitment of above-mentioned cooling capacity, the preparation cooling alleviates with the cooling load of cooler 80, can seek the energy-conservation of dehumidifier/air-conditioning system integral body.

In addition, in the present embodiment, based on the temperature of the processing air that is cooled off by aerial cooler 35,36 and carry out the volume controlled of heat pump 30, flow into the temperature stabilization of air of the processing region 11 of dehumidifying rotor 10 thus, the result can stably hang down the supply of dew point air.

In addition, in the present embodiment,, therefore can be heated to by heat pump more than 90 maximum temperatures that can heat of regeneration air because electric heater 70 is set.Thus, the moist composition of dehumidifying member reduces during owing to rotor regeneration, therefore can supply with the low dew point air of-50 ℃ of grades.In addition, the temperature sensor 79 that setting can detect the temperature of the regeneration air that heated by this heater 70, and in the mode that the temperature of this regeneration air becomes certain value the heat that adds of electric heater 70 is controlled.Even under the situation of the operating condition conversion of heater 30, also can make the temperature stabilization of regeneration air, and guarantee the dehumidifying effect of processing region 11, and can stably carry out the supply of above-mentioned low dew point air thus.

In addition, in the present embodiment, become following structure: the refrigerator 80 of the outer gas 91 that imports being assisted cooling promptly is set, and the in shortage of cooling capacity based on heat pump 30 compensated.For this reason, can be the capacity that energy that regeneration air 95 temperature can reclaim when rising is set the circulation of heat pump 30 accordingly with the heat that adds in the air heater 32.Therefore, can play following effect: promptly prevent from heat unit to reduce because of the heating efficiency of the heat pump 30 superfluous energy utilization efficiency that causes.

About this effect, use Fig. 3 to be illustrated.Fig. 3 is the figure that the heating and cooling energy needed of the air in the related dehumidifier/air-conditioning system of present embodiment is compared with other modes.(1)~(3) each mode is following such structure.Structure (1) expression utilizes electric heater 70 fully and carries out the heating of the regeneration air in the dehumidification system, and utilizes refrigerator 80 fully and handle the cooling of air, and does not use the situation of heat pump.Next, structure (2) is to utilize the evaporimeter of heat pump 30 fully and the cooling of handling air, and the heating of regeneration air is undertaken by the heat unit and the electric heater 70 of heat pump 30, and does not use the situation of refrigerator 80.

Structure (3) is the structure of present embodiment, is to pine for using heat pump 30 and electric heater 70 in adding of regeneration air like that as the aforementioned, and uses the situation of heat pump 30 and cooler 80 in the cooling of handling air.In addition, suppose in structure (2), be provided with in the employed heat pump outside gas cooler 33, and be in the scope of the present invention.

In Fig. 3, suppose that catabiotic in the structure (1) comprehensively is 100%, and the consumed energy in each structure is categorized into each key element machine and compares.In the comparison of (1) and (2), handle the cooling energy needed of air, refrigerator with respect to (1), (2) heat pump increases significantly, this be because, with employed cooling medium in the refrigerator 80 is that the cooling medium of substitute fluorine system is relative, and employed cooling medium is theoretical achievement (reason Theory the becomes Performance) carbon dioxide that coefficient is low in the heat pump 30.

Yet, in (2), by carrying out heating based on the regeneration air of heat pump 30, the consumed energy of electric heater 70 such minimizing as shown, energy consumption reduces more than (1) as a result.Even this expression under the situation of not using refrigerator 80, is provided with the heat pump 30 of outer gas cooler 33 by employing, can seek to save energy.

Next, in the comparison of (2) and (3), owing to correspondingly set the ability of heat pump 30 with callable heat in the regeneration air, so the consumption electric power of heat pump 30 reduces, and the consumption electric power of the refrigerator 80 that the cooling heat to the processing air of the deficiency of this exchange compensates has taken place.In addition, electric heater 70 all be used to from by 30 pairs of regeneration airs of heat pump the maximum temperature that can heat further to the purposes of high temperature heating, therefore in (2) and (3), do not have difference.

In complete catabiotic comparison, the structure of present embodiment is that (3) are with respect to (2) further minimizing.This is because following cause: promptly ability and the cooling load because of heat pump 30 correspondingly is set in (2), so heating efficiency surplus, because of its energy is released to the loss that outer gas causes, and carry out an air cooled part by achievement (become Performance) the high refrigerator 80 of coefficient.In addition, for the middle situation that increases the cooling load of refrigerator 80 and reduce the capacity of heat pump 30 of structure (3), because the structure of system approaches (1) so consumed energy increases.

In addition,, therefore have the steady load of heat pump, can guarantee the advantage point that adds heat in the air heater 32 owing to, can carry out correspondence by the volume controlled of refrigerator 80 to the outer air cooling load change but that causes by season by refrigerator 80 is set.For example, the temperature degree is low outside, under the little situation of cooling load, by refrigerator 80 cutting out and can realizing correspondence.

In addition, by detected value (detected value of temperature sensor 89) based on the temperature of the outer gas 91 that leads to aerial cooler 36 from cooling spiral pipe 81, and the startup of carrying out refrigerator 80 stops and volume controlled, and only provide outer air cooling to surpass the part of the maximum capacity of heat pump 30 in loading by utilizing refrigerator 80, can guarantee to maximum limit the running ability of heat pump 30 thus, and the heat that adds in the air heater 32 is changed to maximum, and the input of electric heater 70 reduced, thereby can bring into play energy-saving effect shown in Figure 3.

In addition, though in the present embodiment with employed drier dehumidifier in the dehumidification system as cleaning-type, even but above-mentioned spy is driven the such drier dehumidifier that does not have the standard type of cleaning the zone disclosed in the 2005-34838 communique, also can access same effect.That is to say, not only drive the heater that the heat unit that makes heat pump the 2005-34838 communique becomes the air that imports as handling air as special, and be provided with such as making the cooling medium to handling after air heats further reduce the such outer gas radiator of temperature by the air that imports cooling usefulness, also can seek the increase and the whole energy of device of cooling capacity and save.

(embodiment 2)

Next, for other embodiment of the present invention, use Fig. 4~Fig. 7 and illustrate.Fig. 4 is the overall system view of the related dehumidifier/air-conditioning system of present embodiment, and Fig. 5 is the figure that represents employed heat pump cycle in the present embodiment on temperature-heat content line chart.Fig. 6 is the curve map of the relation of the consumption electric power of the related dehumidifier/air-conditioning system of the temperature efficiency of employed inner heat exchanger and present embodiment in the expression present embodiment etc.Fig. 7 is the consumed energy of dehumidifier/air-conditioning system that present embodiment is related and the curve map of three kinds of systematic comparisons among detailed and Fig. 3 thereof.In figure separately, for the structural element identical with the embodiment of Fig. 1, the additional symbol identical with Fig. 1.In addition, in the following description, concentrate on present embodiment and Fig. 1 embodiment dissimilarity and describe.

As shown in Figure 4, the related dehumidifier/air-conditioning system of present embodiment is with respect to the embodiment of Fig. 1, refrigerator 80 and the cooling spiral pipe 81 and the temperature sensor 89 that are attached to it are not set, and become following structure: promptly in the circulation of heat pump 30, be arranged on by the cooling medium of the supercriticality of outer gas radiator 33 coolings and utilize aerial cooler 36 external gas to cool off and become the inner heat exchanger 38 that carries out heat exchange between the cooling medium of cooling medium steam.In addition, become the structure that pressure-reducing valve 34 is arranged on the downstream side of inner heat exchanger 38.

In the dehumidifier/air-conditioning system of present embodiment, the outer gas 91 that imports as using to gas, directly cooled off by aerial cooler 36, and with cooled off by aerial cooler 35 indoor return gas 94 interflow after, with the embodiment of Fig. 1 similarly a part become scavenging air 92, rest parts is dehumidified by dehumidifying rotor 10 and is become to gas 93.The system of scavenging air 92 and regeneration air 95 and the embodiment of Fig. 1 are same.

Action with the heat pump 30 in the thick line among Fig. 5 (4) the expression present embodiment.Mark P~W similarly represents the state of cooling medium with the mark A~F among Fig. 2.Rise and become state P by the boost cooling medium Yin Wendu that is supercritical pressure of compressor 31, and through air heater 32, outer gas radiator 33 and after becoming state R, in inner heat exchanger 38 to giving heat and become state S to the cooling medium steam of compressor 31 from aerial cooler 36.Thereafter, become two-phase state T by expansion valve 34, in aerial cooler 35,36, become behind saturated vapor U, the superheated steam V and in inner heat exchanger 38, further be heated and temperature rises and after becoming state W, is inhaled into the suction side of compressor 31.

If the circulation with the embodiment of the Fig. 1 shown in the dotted line among the heat pump cycle in the present embodiment and Fig. 5 is compared, then cooled off to state S from state R by cooling medium in the inner heat exchanger 38 after 33 heat releases of outer gas radiator, thus, the cooling capacity of the per unit cooling medium amount in the aerial cooler 35,36 from the QE shown in the figure to QE " increase.This effect mainly by known is usually, uses the increase of refrigerating effect of internal heat exchange of the freeze cycle of carbon dioxide as cooling medium.

In addition, in the present embodiment, the cooling medium steam that is directed to compressor 31 is heated by inner heat exchanger 38 and the temperature rising.Here, compressor spue pressure with the embodiment same case of Fig. 1 under, the temperature that spues of compressor rises, but in the present embodiment by set the pressure that spues of compressor than the lowland, can make the temperature that spues identical with the embodiment of Fig. 1.Therefore, the compression ratio of compressor 31 is compared with the embodiment of Fig. 1 and is become less.Here and since the efficient of compressor usually under the less situation of compression ratio better, therefore in the present embodiment because the reduction of pressure and pressure ratio that spues, and make the efficient of compressor rise, and can further reduce consumption electric power.Next, use Fig. 6 that their relation is described.

Fig. 6 is with the temperature efficiency ε of transverse axis as inner heat exchanger 38, with the ratio of the longitudinal axis as consumed power and compression ratio, and with compression ratio together and the compressor efficiency that changes, and the temperature that spues of compressor 31 be changed to certain value and represent the figure of their relation.Point in temperature efficiency ε=0 is illustrated under the situation that inner heat exchanger 38 is not set among Fig. 4, promptly with Fig. 3 in (2) identical structure.Heat pump cycle on the T-h line chart in, same with the embodiment of Fig. 1, become in Fig. 2 or Fig. 5 with the represented circulation of dotted line.The inner heat exchanger 38 of the heat pump 30 in the present embodiment, when running of fixing on transverse axis, to move by (4) represented temperature efficiency.

At first, represent only to consider the increase of described refrigerating effect with fine rule, promptly compressor efficiency calculates the result of the consumption electric power of dehumidifier/air-conditioning system integral body as certain value.If the temperature efficiency of inner heat exchanger increases, the effect that increases by means of the cooling capacity of per unit cooling medium amount then, the work of compressor alleviates, and the consumption electric power of entire system reduces.

Next, be represented by dotted lines the variation of the compression ratio of this moment.Increase with temperature efficiency ε and the inlet temperature of compressor rises correspondingly, the result of the pressure of determining to spue the fixing mode of temperature to spue is that spue pressure and compression ratio reduce as shown in Figure 6.The result of the compressor efficiency η that derives by this compression ratio shown in broken lines among Fig. 6.In addition, the relation of compression ratio and compressor efficiency is put down into by for example described NEDD shown in the formula p.106 (5.1-4) etc. of 13 annual inquiry reports.As shown in the figure, the increase of the temperature efficiency of compressor efficiency and internal heat exchange 38 is together risen.

The rising of in Fig. 6, using thick line to show to have considered this compressor efficiency and result after the consumption electric power of dehumidifier/air-conditioning system integral body calculated again.By inner heat exchanger 38 is set, compressor efficiency rises, and with by represented reduce effect and compare of fine rule because of cooling capacity increases caused consumed power, consumed power further reduces.In (4) as the operation condition of present embodiment, compare with the situation of saving inner heat exchanger, can access about 15% consumption electric power and reduce effect.

If the heating and cooling energy needed of the air of the dehumidifier/air-conditioning system that present embodiment is related compares with three kinds of systems that compared among Fig. 3, then become shown in Figure 7.As can be known, by the reduction effect of consumption electric power discussed above, can further reduce consumption electric power with respect to the embodiment of Fig. 1.

As discussed above, in the present embodiment, by in heat pump 30, appending heat exchanger 38, except the increase effect of known usually cooling capacity can also obtain the raising of the compressor efficiency that the reduction by compression ratio causes and the reduction effect of the consumption electric power that accompanies therewith.That is to say, with the embodiment of Fig. 1 mutually ratio piston compressor spue and press and compression ratio can access the equal compressor temperature that spues lower the time, this is the bigger feature of present embodiment on the one hand, is the effect that heat pump cycle is used for the uniqueness that produced under the situation of dehumidifier/air-conditioning system.

In addition we know, though do not use refrigerator 80 in the present embodiment, the heat pump of the dehumidifier/air-conditioning system of the use refrigerator 80 such with respect to the embodiment of Fig. 1 appends inner heat exchanger 38 and also can reach same effect.In addition, as present embodiment, do not using under the situation of refrigerator 80, system is oversimplified and makes the cooling medium of heat pump 30 is carbon dioxide, do not need the cooling mediums such as substitute fluorine that use the greenhouse effects of the earth coefficient high thus, and can as one man obtain the very favourable dehumidifier/air-conditioning system in environmental protection aspect with catabiotic reduction effect.

Among each embodiment shown in above, the cooling medium of heat pump 30 carries out heat release with supercritical pressure in air heater 32, therefore regeneration air 95 can be heated to high temperature, and can be shown in the comparison of (2) (3) (4) of structure among Fig. 3 or Fig. 7 (1) and enforcement of the present invention reduce the consumption electric power of electric heater 70 and realize the energy-saving effect of dehumidifier/air-conditioning system integral body like that.

In addition, among each embodiment shown in above,, be 31.1 ℃ lower carbon dioxide owing to use critical-temperature as the cooling medium of heat pump 30, therefore the high-pressure side of circulation easily becomes supercriticality, and can access the effect that is caused by the heat release in the above-mentioned supercriticality.In addition, as is generally known its greenhouse effects of the earth coefficient is minimum like that owing to carbon dioxide, therefore can access the recovery that do not need cooling medium, with the corresponding dehumidifier/air-conditioning system of environmental problem.

In addition, among each embodiment shown in above, owing to becoming following structure: i.e. gas radiator 33 outside the cooling body of the cooling medium of conduct after air heater 32 is discharged is provided with, and, therefore has the advantage that does not need cooling water system equipment by the mechanism that heat release is cooled off with outer gas 99.

On the other hand, importing under the situation of native system in the factory for preparing cooling water system in advance etc., also can be following structure: promptly substitute outer gas radiator 33 and water-cooled cooling medium cooler is set, and cool off by cooling water.At this moment, as needing substituting of water-cooling system, and compare and can cool off with less heat transfer area with the outer gas radiator 33 of air-cooled type, therefore having can be with the advantage of cooling medium and dehumidifier/air-conditioning system miniaturization.In addition, this cooling water also can be river or seawater etc. as can be known.

(embodiment 3)

Use Fig. 8 the 3rd embodiment to be described to Figure 12.Fig. 8 is the overall system view of the related dehumidifier/air-conditioning system of present embodiment.Fig. 9 is the figure that represents employed heat pump cycle in the present embodiment on temperature one heat content line chart.Figure 10 is the figure of the cellular construction of expression present embodiment.In addition, Figure 11 is consumed energy and the detailed detailed map of with the situation of use heat pump comparing thereof of summer in the peak value condition of dehumidifier/air-conditioning system that present embodiment is related.In addition, Figure 12 is the curve that the moon other mean consumption energy and Figure 10 that present embodiment is related similarly do not use the situation of heat pump to compare.

In Fig. 8, be with Fig. 1 difference, output at refrigerator 80 is on the direct-expansion type cooling spiral pipe (the first cooling spiral pipe) 81 open and close valve 83 to be set, and indoor returning on the direct-expansion type cooling spiral pipe (the second cooling spiral pipe) 82 that gas 94 cools off is being provided with open and close valve 84.In addition, the aerial cooler 36 that is connected on the heat pump 30 is not set, and becomes and utilize 80 pairs of refrigerators to return by aerial cooler 35 indoor that gas 94 further cools off and supply to the structure of dehumidifying rotor 10 with outer gas 91.In addition, as substituting of sensor 89 is set, dual-purpose temperature sensor 39 and be used for the control of refrigerator.Other structure is identical with Fig. 1.

Therefore, the basic action to the related dehumidifier/air-conditioning system of present embodiment describes.In dehumidifier/air-conditioning system, utilization is located at the first cooling spiral pipe on the refrigerator 80 and the outer gas 91 (processing air) that imports is cooled off, and utilize the aerial cooler 35 of heat pump 30 and refrigerator 80 the second cooling spiral pipe 82 and to cooling off, and with they interflow from the low indoor indoor gas 94 that returns of dew point.Processing air behind this interflow, such as described above, a part is directed to cleaning zone 13 as scavenging air 92 along separate routes, and all the other are directed to processing region 11 and after reducing humidity, are directed to the air conditioning chamber as giving gas 93.In addition, at the open and close valve 83 (magnetic valve) that from the pipe arrangement way of refrigerator 80 to first cooling spiral pipes 81, is provided for controlling cooling medium, from the pipe arrangement way of refrigerator 80 to second cooling spiral pipes 32, open and close valve 84 (magnetic valve) is being set equally.

On the other hand, scavenging air 92,13 pairs of dehumidifying rotors 10 cool off in the cleaning zone.Thus, as with as the feature of cleaning-type drier dehumidifier and by known, only from being undertaken to gas by cooled zones fully, the result can access humidity low in the extreme give gas.Because of dehumidifying rotor 10 being cooled off the scavenging air 92 that temperature rises, become regeneration air with recirculation regeneration air 96 interflow, and after heating in turn by air heater 32, the electric heater 70 of heat pump 30, be directed to regeneration zone 12 and removing from the moisture of dehumidifying rotor 10 promptly carried out in regeneration.

From the regeneration air 95 of regeneration zone 12, a part is collaborated with scavenging air 92 along separate routes and as recirculation air 96 as described above, and remaining is discharged to outside the machine as exhaust 97 in the lump with the moisture of removing from dehumidifying rotor 10.

Next, use Fig. 9 that the action of the heat pump 30 of this moment is described.In the present embodiment, as the action medium use carbon dioxide of heat pump 30, the mark A~F among Fig. 9 represents the state of the cooling medium on temperature shown in Figure 9-heat content line chart, and curve H represents saturated line.

Be compressed to the cooling medium of supercritical pressure by compressor 31, Yin Wendu rises and becomes state A, and is directed to air heater 32.In air heater 32, coolant temperature descends and regeneration air 95 is heated and becomes state B, and is directed to outer gas radiator 33.In the gas radiator 33, the heat release that is imported into is lower than the regeneration air temperature that flow in the air heater 32 with outer gas 99 outside, and coolant temperature further reduces and becomes state C.Thereafter, cooling medium is directed to expansion valve 34 and reduces pressure, and the two-phase state that becomes cooling medium liquid and cooling medium vapour composition is state D, in aerial cooler 35, utilizes the evaporation latent heat of cooling fluid and the indoor gas 94 that returns is cooled off.All cooling medium liquid evaporation in aerial cooler 35 and become state E on the saturated line, and by after becoming the state F of superheated steam with the indoor heat exchange of returning gas 94 attracted to compressor 31 and is compressed once more.

In addition,, omitted its influence among Fig. 9 and on the isobar of supercritical range, shown state A, B, C, and on the isobar of the gentle body region in two-phase zone, shown D, E, F though in fact have the pressure loss in each heat exchanger.

Figure 10 is the cellular construction of the dehumidifier/air-conditioning system in the expression present embodiment, and the situation that is provided with of each inscape of heat pump.Dehumidifier/air-conditioning system roughly is made of heat extraction unit 101 and dehumidifier unit 102.On heat extraction unit 101, compressor having internally mounted 31, outer gas radiator 33, make ventilate fan 38 to outer gas radiator 33 of outer gas, and expansion valve 34 etc.

In addition, air heater 32, aerial cooler 35 are set in the inscape at heat pump cycle on the dehumidifier unit 102.In addition, though in Figure 10, do not illustrate, but on dehumidifier unit 102, the built-in first cooling spiral pipe 81, the second cooling spiral pipe 82 and making by dehumidifying rotor shown in Figure 8 10, electric heater 70, refrigerator 80 handled air and regeneration air ventilate conduit on them and fan etc.And the cooling medium pipe arrangement 37 that forms heat pump cycle connects heat extraction unit 101, dehumidifier unit 102.

Next, the running control to the dehumidifier/air-conditioning system of present embodiment describes.For outer gas variation of temperature, by the volume controlled of refrigerator 80, and will supply to the temperature of processing air of the processing region 11 of dehumidifying rotor 10, be maintained almost fixed.This handles air, is the air that cooled off by the first cooling spiral pipe, 81 external gas 91 and aerial cooler 35 by heat pump 30, and returns the Air mixing gas that gas cools off by 82 pairs of the second cooling spiral pipes of refrigerator 80 are indoor.Therefore, by cooling load in the air conditioning chamber and the indoor variations in temperature of returning gas 94 time, can tackle by the volume controlled of refrigerator 80.

In addition, even for making the cooling medium outlet temperature of outer gas radiator 33 change because of the change of outer temperature degree and, also can controlling and tackle by the heat of refrigerator 80 owing to its influence makes the situation that the cooling heat of aerial cooler 35, the indoor outlet temperature of returning gas 94 change.In addition, accompany the heating quantitative changeization of the regeneration air 95 in the air heater 32 with the variation of this heat pump cycle.Relative with this variation, the heat control by electric heater 70 can remain the regeneration air temperature by 79 instrumentations of temperature sensor fixing and tackles.

Therefore, under the less situation of the influence that the change of temperature degree and indoor load outside applies heat pump cycle, in the running of native system, heat pump is with almost fixed output and turn round.In addition, the capacity of heat pump is set as follows: the indoor cooling load of returning gas 94 that is determined by the design temperature in the air conditioning chamber etc. that makes that the cooling capacity of aerial cooler 35 sets when being lower than by plan.

Next, use Figure 11, Figure 12 that the energy-saving effect of present embodiment is described.Figure 11 is the result of calculation to the consumption electric power of the dehumidifier/air-conditioning system in the summer peak value, the situation (use of heat pump: do not have) of not using heat pump 30 is promptly only carried out outer gas 9 and the indoor cooling of gas 94 and the situation of only carrying out the heating of regeneration air 95 with electric heater 70 returned with refrigerator 80, with the situation of using heat pump 30, the figure that compares.As shown in Figure 11, the importing owing to heat pump makes consumption electric power cut down about 10%.

In addition, Figure 12 is to each month in the period of one, uses temperature on average between January of certain region and offsets power consumption power and carry out result calculated.In Figure 12, recorded and narrated the comparison during peak value in shown in Figure 11 summer in the lump.In addition, as shown in Figure 12, consume that electric power does not rely on season and the reduction that obtains almost fixed.This is because following cause: promptly because the load of the heating of heat pump, cooling is almost fixed in the period of whole, therefore heat pump is often turned round with rated capacity.

Shown in above in such present embodiment, owing to return on the stream of gas running through there is cooling load in the period of whole one indoor, the aerial cooler 35 of heat pump 30 is set, therefore heat pump in the period of operating condition stable, and as shown in Figure 12, can in the period of running through whole one, realize energy-saving effect.In the present embodiment, can be at the reduction that runs through the consumption electric power shown in Figure 11 of realization in the period of since intergrade and winter total consumption electric power reduction reduce, so reduction rate surpasses 10%.As a result, running through consumption electric power reduction rate in the period of one also more than 10%.

In addition, according to present embodiment, owing to setting the capacity of heat pump 30 to be no more than the indoor value of returning the cooling load of gas, therefore compare with the situation of the cooling load of bearing outer gas, the scale of device is less, and can suppress the rising of initial cost.In addition, because the operating condition of heat pump 30 is stable, therefore promptly to add heat be stable in the period of running through one to the operating condition of the such electric heater 70 shown in the situation that the use of the heat pump among Figure 12 " has ", and can cut down the capacity of electric heater 70 and realize miniaturization.

In addition, because these machines carry out work effectively in the period of running through one, so energy-saving effect is big with respect to the increase change of initial cost.

In addition, in the present embodiment, become following structure: the refrigerator 80 that the outer gas 91 that imports is cooled off promptly is set, and for fixing mode refrigerator 80 is controlled with the temperature of the processing air of the processing region 11 that supplies to dehumidifying rotor 10, therefore can with the change of outer temperature degree irrespectively, stable low humidity air is supplied to by the air-conditioning object, and can make the operating condition of heat pump 30 also stable.

In addition, in the present embodiment, the second cooling spiral pipe 82 that cools off again by the part that the cooling capacity of utilizing refrigerator 30 is set, and the indoor gas 94 that returns that the aerial cooler 35 by heat pump 30 is cooled off is cooled off again, even therefore for the change of indoor load outside the change of temperature degree, also can not make the operating condition of heat pump 30 carry out correspondence with changing.

In addition, in the present embodiment, heat unit as heat pump 30, except the air heater 32 that regeneration air 95 is heated, outer gas radiator 33 also is set, therefore as shown in Figure 9, aerial cooler 35 is the heat content of the cooling medium of evaporator inlet is reduced to state C from the value of a state B shown in Figure 9 value.Cooling capacity in the aerial cooler as a result, poor from the heat content of state B and state F under the situation of gas radiator 33 outside not being provided with, the difference that increases to the heat content of state D and state F is QE shown in Figure 9.Therefore, the freezing load of cooler 80 is alleviated, and can realize the miniaturization of refrigerator 80 and energy-conservation effect.

In addition, in the present embodiment, by the heat extraction unit 101 that includes compressor 31, outer gas radiator 33, fan 38 etc., and the dehumidifier unit 102 that includes dehumidifying rotor 10, air heater 32, aerial cooler 35 etc. constitutes dehumidifier/air-conditioning system integral body, therefore exhaust unit 101 can be arranged on outdoorly, be arranged on dehumidifier unit 102 outdoor.

Can make from dehumidifier unit 102 and to handle the air circulation this point, have by being arranged on Machine Room etc. indoor and do not need the advantage of waterproof construction.On the other hand, low more from the cooling medium outlet temperature of outer gas radiator 33 in the heat extraction unit 101, the cooling capacity QE of aerial cooler shown in Figure 9 increases more, and the load of refrigerator 30 alleviates and energy-conservation more.Therefore, outdoor by heat extraction unit 101 is arranged on, can be to the outer gas venting lower than mechanical indoor air temperature, this energy-saving effect becomes big thus.Can obtain these advantage points simultaneously in the present embodiment.

In addition, in the present embodiment, the cooling medium of heat pump 30 carries out heat release with supercritical pressure in air heater 32, therefore in air heater 32 cooling medium when temperature reduces continuously to regeneration air 95 heat releases, and can carry out heat exchange with the convection (subtend flow pattern) of regeneration air 95, and shown in the comparison that the use of the heat pump among Figure 11 and Figure 12 " has " " nothing " like that, because of the consumption electric power of electric heater 70 reduces the energy-saving effect that can realize dehumidifier/air-conditioning system integral body.

In addition, in the present embodiment, as the cooling medium of heat pump 30, owing to use critical-temperature to be low to moderate 31.1 ℃ carbon dioxide, therefore the high-pressure side of circulation becomes supercriticality easily, and can access the effect that is caused by above-mentioned heat release in overcritical.In addition, as known, the greenhouse effects of the earth coefficient of carbon dioxide is minimum, therefore there is no need to carry out the recovery of cooling medium, can access and the corresponding dehumidifier/air-conditioning system of environmental problem.

In addition, among each embodiment shown in above, gas radiator 33 as the cooling body of the cooling medium after air heater 32 comes out and outside being provided with, and become the structure of cooling off with outer gas 99 by heat release, therefore have the advantage that does not need cooling water system.

On the other hand, when in the factory of purchasing cooling water system in advance etc., importing native system, water-cooled cooling medium cooler also can be set and substitute outer gas radiator 33, and become the structure of cooling off by cooling water.In this case, as needing substituting of cooling water system, can cool off to compare with less heat transfer area with the outer gas radiator 33 of air-cooled type, therefore having can be with the advantage of cooling medium cooler and dehumidifier/air-conditioning system miniaturization.In addition, this cooling water also can be river or seawater as can be known.

(embodiment 4)

Next, use Figure 13 that the 4th embodiment of the present invention is described.The dehumidifier/air-conditioning system of Figure 13 is the structure roughly the same with Fig. 8, but following point is different.In the embodiment of Fig. 8, by the 2nd cooling spiral pipe 82 the indoor gas 94 that returns from indoor recirculation is cooled off, relative therewith, in the present embodiment, utilize the processing air behind described indoor outer gas 91 interflow of returning gas 94 and importing from the outside of 82 pairs of the 2nd cooling spiral pipes to cool off.

In the present embodiment, become by means of 82 pairs of the second cooling spiral pipes and flow into the structure that the processing air before the processing region 11 of dehumidifying rotor 10 cools off.Thus, compare with embodiment 3, volume controlled that can be by refrigerator 80 will stably be controlled near the desired value by the detected rotor intake air temperature of temperature sensor 39.In the dehumidifying rotor of member that keeps like that as described above dehumidifying, wet-out property is affected because of the inlet temperature of handling air, therefore in the present embodiment because this inlet temperature is stable, therefore has the stable low desired value advantage nearby that controls to of the temperature and humidity that the rotor outlet air promptly can be given gas 93.This is needing as manufacturing process such as semiconductor and display in the purposes of low-humidity environment, and is very important from the viewpoint that the production quality makes progress.

In addition, the heat pump cycle in the present embodiment, consume electric power and consume electric power one in the period of change represent by Fig. 9, Figure 11 and Figure 12 respectively same the branch with the 3rd embodiment, and can access same effect.And, also can become the structure same, and can access the effect identical with the 3rd embodiment with Figure 10.

Claims (20)

1, a kind of dehumidifier/air-conditioning system is characterized in that,
Have:
Purification type drier dehumidifier, it makes passing through in turn as lower area of purchasing on the dehumidifying rotor by dehumidifying rotor rotation: promptly the processing region that the moisture of handling air is absorbed, this moisture is released to the regeneration zone of high temperature regeneration air and uses tempering air the purification zone that the zone that emits moisture cools off of rising of Yin Wendu in the regeneration zone;
Heat pump, it has endothermic section and heat unit;
Cooler, it cools off as cooling source described endothermic section to the described air that is dehumidified of waiting;
Heater, it as heating source, and heats at the regeneration zone entrance side described heat unit to described regeneration air,
Described heat unit constitutes by emitting the first hot radiator to described regeneration air and emitting the second hot radiator to outside cooling medium.
2, according to the described dehumidifier/air-conditioning system of claim 1, it is characterized in that,
Described heat pump is provided with the inner heat exchanger that carries out heat exchange between the cooling medium that carries out the cooling medium of heat release by described the 2nd radiator and absorbed heat by described endothermic section.
3, according to claim 1 or 2 described dehumidifier/air-conditioning systems, it is characterized in that,
The temperature that is provided with the described processing air after being cooled in cooler detects, and carries out the control device of the volume controlled of described heat pump.
4, according to each described dehumidifier/air-conditioning system in the claim 1~4, it is characterized in that,
Become following structure: promptly be provided with heating arrangements again, described heating arrangements more further heats after in described first radiator described regeneration air being heated, and with regeneration air from this again heating arrangement import to the regeneration zone of described drier dehumidifier.
5, according to the described dehumidifier/air-conditioning system of claim 4, it is characterized in that,
Be provided with by detecting temperature by the described again regeneration air that heating arrangements heated, and to the control device that heat is regulated that adds of this heating arrangements.
6, according to the described dehumidifier/air-conditioning system of claim 5, it is characterized in that,
Be provided with the auxiliary cooling body that described processing air is cooled off.
7, according to the described dehumidifier/air-conditioning system of claim 6, it is characterized in that,
Be provided with the temperature sensor that the temperature by the processing air that described auxiliary cooling body cooled off is detected, and be provided with and be used to stop or the control device of volume controlled from the startup that described auxiliary cooling body is carried out in the output of this temperature sensor.
8, according to the described dehumidifier/air-conditioning system of claim 7, it is characterized in that,
Described external refrigeration medium is an air.
9, described according to Claim 8 dehumidifier/air-conditioning system is characterized in that,
Described external refrigeration medium is a cooling water.
10, according to the described dehumidifier/air-conditioning system of claim 9, it is characterized in that,
The cooling medium of described heat pump carries out heat release in described heat unit with supercritical pressure.
11, according to the described dehumidifier/air-conditioning system of claim 10, it is characterized in that,
The cooling medium of described heat pump is a carbon dioxide.
12, a kind of dehumidifier/air-conditioning system is characterized in that,
Have:
Purification type drier dehumidifier, it has on dehumidifying rotor: processing region that the moisture of handling air is absorbed and the regeneration zone that this moisture is released to the regeneration air of high temperature, and by means of described dehumidifying rotor rotation, described processing region and described regeneration zone pass through in turn;
Heat pump, it has endothermic section and heat unit;
Aerial cooler, it cools off as cooling source described endothermic section to the described air that is dehumidified of waiting;
Air heater, it as heating source, and heats at the regeneration zone entrance side described heat unit to described regeneration air,
Described processing air be the outer gas that imports from the outside with from leading and the indoor mixing air that returns gas of recirculation as the indoor of air-conditioning object, and on the described indoor stream that returns gas, be provided with the aerial cooler of described endothermic section as cooling source.
13, a kind of dehumidifier/air-conditioning system is characterized in that,
Have:
Purification type drier dehumidifier, it has processing region that the moisture of handling air is absorbed on dehumidifying rotor, this moisture is released to high temperature regeneration air regeneration zone and use tempering air that Yin Wendu in the regeneration zone is risen and emit the purification zone that cool off in the zone of moisture, and by means of described dehumidifying rotor rotation, described each zone is passed through in turn;
Heat pump, it has endothermic section and heat unit;
Aerial cooler, it cools off as cooling source described endothermic section to the described air that is dehumidified of waiting;
Air heater, it as heating source, and heats at the renewing zone entrance side described heat unit to described regeneration air,
Wherein, described processing air is from the outer gas of outside importing and from leading and the indoor mixing air that returns gas of recirculation as the indoor of air-conditioning object, on the described indoor stream that returns gas, be provided with the aerial cooler of described endothermic section as cooling source, and refrigerator is set, described refrigerator with the upstream side of the described indoor portion of mixing that returns gas to described importing outside gas cool off.
14, according to the described dehumidifier/air-conditioning system of claim 13, it is characterized in that,
Described refrigerator is cooling off with the upstream side of the described indoor portion of mixing that the returns gas outer gas to described importing, and with described importing outside before the interflow of gas or behind the interflow, to by with the endothermic section of described heat pump the indoor gas that returns that described aerial cooler cooled off, cool off again as cooling source.
15, according to the described dehumidifier/air-conditioning system of claim 14, it is characterized in that,
The heat unit of described heat pump, by constituting as lower member: i.e. air heater, it is as the heating source of described regeneration air and to the regeneration air heat release; And outer gas radiator, it emits heat to outside cooling medium.
16, a kind of dehumidifier/air-conditioning system is characterized in that,
Have:
Purification type drier dehumidifier, it has processing region that the moisture of handling air is absorbed and this moisture is released to the regeneration zone of the regeneration air of high temperature on dehumidifying rotor, and by means of described dehumidifying rotor rotation, described each zone is passed through in turn;
Heat pump, it has endothermic section and heat unit;
Cooler, it cools off as cooling source described endothermic section to the described air that is dehumidified of waiting;
Described heat unit is by the air heater that described regeneration air is heated at the regeneration zone entrance side; And the outer gas radiator that heat is released to the external refrigeration medium constituted, and by as lower member constituent apparatus integral body: promptly by as described in the endothermic section of dehumidifying rotor, heat pump be the dehumidifier that the air heater etc. of cooler and heat pump constitutes; The heat extraction unit that constitutes by described compressor and described second radiator etc.; And connect their cooling medium pipe arrangement etc.
17, according to the described dehumidifier/air-conditioning system of claim 16, it is characterized in that,
Respectively described dehumidifier unit is arranged on indoorly, is arranged on described heat extraction unit outdoor.
18, according to the described dehumidifier/air-conditioning system of claim 16, it is characterized in that,
Described external refrigeration medium is air or water.
19, according to the described dehumidifier/air-conditioning system of claim 16, it is characterized in that,
The cooling medium of described heat pump carries out heat release with supercritical pressure in described heat unit.
20, according to the described dehumidifier/air-conditioning system of claim 19, it is characterized in that,
The cooling medium of described heat pump is a carbon dioxide.
CNA2007100016955A 2006-01-13 2007-01-12 Dehumidifying air conditioning system CN101000163A (en)

Priority Applications (3)

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JP2006005474 2006-01-13
JP2006005474A JP4591355B2 (en) 2006-01-13 2006-01-13 Dehumidification air conditioning system
JP2006159201 2006-06-08

Related Child Applications (1)

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CN106564979A (en) * 2015-10-08 2017-04-19 中国科学院大连化学物理研究所 Integrated refrigeration, dehumidification and pure water preparation system using solar energy or low-temperature heat source
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CN101889177A (en) * 2007-12-07 2010-11-17 大金工业株式会社 Humidity control device
US8875540B2 (en) 2007-12-07 2014-11-04 Daikin Industries, Ltd. Humidity control apparatus
CN101889177B (en) * 2007-12-07 2013-06-19 大金工业株式会社 Humidity control device
CN102197265A (en) * 2008-11-07 2011-09-21 洋马株式会社 Desiccant air conditioning device
CN102197265B (en) * 2008-11-07 2014-08-06 洋马株式会社 Desiccant air conditioning device
CN102160898B (en) * 2010-02-12 2014-07-16 松下电器产业株式会社 Ion generating device
CN102160898A (en) * 2010-02-12 2011-08-24 松下电器产业株式会社 Ion generating device
CN103827589A (en) * 2011-09-29 2014-05-28 大金工业株式会社 Dehumidification system
CN103827589B (en) * 2011-09-29 2016-10-19 大金工业株式会社 Dehumidification system
CN103574833A (en) * 2012-07-30 2014-02-12 (株)Ck首露绅 Mixed operation device and mixed operation method of regenerative heater
CN103977675B (en) * 2014-04-30 2018-01-23 广东工业大学 A kind of adsorption and dehumidification process and device
CN106091175A (en) * 2015-04-28 2016-11-09 株式会社西部技研 Low dew point hothouse low-temp recovery desiccant dehumidification system
CN106091175B (en) * 2015-04-28 2020-05-12 株式会社西部技研 Low-temperature regeneration drying and dehumidifying system for low-dew-point drying chamber
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