WO2002093081A1 - Deshumidificateur - Google Patents
Deshumidificateur Download PDFInfo
- Publication number
- WO2002093081A1 WO2002093081A1 PCT/JP2001/004072 JP0104072W WO02093081A1 WO 2002093081 A1 WO2002093081 A1 WO 2002093081A1 JP 0104072 W JP0104072 W JP 0104072W WO 02093081 A1 WO02093081 A1 WO 02093081A1
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- WIPO (PCT)
- Prior art keywords
- section
- refrigerant
- air
- evaporator
- heat exchanger
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F3/1411—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 by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1423—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 by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F3/1405—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 in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- 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
- F24F5/0007—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 cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1004—Bearings or driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1016—Rotary wheel combined with another type of cooling principle, e.g. compression cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1032—Desiccant wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1056—Rotary wheel comprising a reheater
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1068—Rotary wheel comprising one rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1084—Rotary wheel comprising two flow rotor segments
Definitions
- the present invention relates to a dehumidifier, and more particularly to a dehumidifier having a high dehumidifying ability.
- a compressor 1 for compressing the refrigerant C a condenser 2 for condensing the compressed refrigerant C and heating the processing air A, and decompressing the condensed refrigerant C with an expansion valve 5
- a dehumidifier 11 comprising: an evaporator 3 for evaporating this to cool the processing air A to a temperature equal to or lower than the dew point.
- the evaporator 3 cools the processing air A from the air conditioning space 10 below the dew point, removes moisture in the processing air A, and heats the processing air A cooled below the dew point with the condenser 2 to heat the air A. 10 had been supplied.
- the heat pump HP includes the compressor 1, the condenser 2, the expansion valve 5, and the evaporator 3.
- the heat pump HP pumps heat from the processing air A flowing through the evaporator 3 to the processing air A flowing through the condenser 2.
- the conventional dehumidifier 11 equipped with the heat pump HP as described above could not supply dry air of 4 g / kg DA or less in absolute humidity.
- the operating temperature of the evaporator 3 of the heat pump HP is lower than the freezing point, the dehumidified moisture becomes ice on the heat transfer surface to land on the heat transfer surface, impeding the heat transfer and making continuous operation impossible. That's why.
- the present invention provides a method for continuously supplying dry air having an absolute humidity of 4 g / kg DA or less without dehumidifying air as ice while keeping the dehumidified water on the heat transfer surface of the evaporator of the heat pump as ice.
- the purpose of the present invention is to provide a dehumidifying device that can perform the dehumidification. Disclosure of the invention
- moisture in process air A is adsorbed; A water adsorption device 103; a condenser 220 for heating the regeneration air B upstream of the moisture adsorption device 103 by condensing the refrigerant C, and a regeneration air B for evaporating the refrigerant C.
- Moisture adsorption An evaporator 210 that cools to a temperature below the dew point downstream of the device 103, and a booster 260 that pressurizes the refrigerant C evaporated by the evaporator 210 and sends it to the condenser 220.
- a first heat exchange between the regeneration air B flowing between the moisture adsorption device 103 and the evaporator 210 and the regeneration air B flowing between the evaporator 210 and the condenser 220 A heat pump HP 1 having a heat exchanger 300; and the regeneration air B is configured to be recycled.
- the regeneration air is heated by the condenser, the water content is increased by regenerating the moisture adsorption device, The water is cooled by the heat exchanger, the water content is reduced by the condensation of water, and the water is circulated by the first heat exchanger.
- the regenerated air part of the moisture is condensed due to the cooling by the first heat exchanger, and the moisture content may be reduced.
- it Before being cooled by the evaporator, it is cooled (pre-cooled) by the first heat exchanger, and after being cooled by the evaporator, it is heated (pre-heated) by the heat exchanger. Can be.
- the moisture of the treated air is adsorbed by the moisture adsorbing device, so that the humidity of the treated air is greatly reduced, and dry air can be supplied. Recycling of regenerated air means that the regenerated air after regenerating the desiccant of a desiccant rotor, such as a desiccant rotor, is not exhausted to the atmosphere as it is (it does not need to be exhausted at all, or part of it is exhausted). It means that it is configured to flow through the circulation circuit so that most of it can be reused as regeneration air.
- refrigerant is evaporated and condensed, typically at a pressure intermediate the condensing pressure in the condenser and the evaporating pressure in the evaporator.
- the first heat exchanger 300 is constituted by a group of small tubes that connect the condenser 220 and the evaporator 210 to flow the refrigerant;
- the regeneration air that is configured to guide the refrigerant condensed in 220 to the evaporator 210, and that flows between the moisture adsorption device 103 and the evaporator 210; 0 and the regeneration air flowing between the condenser 220 and the condenser 220 may be configured to alternately contact the regeneration air.
- the connection is a concept that includes indirect connection through a pipe, a pipe joint, or the like.
- the first heat exchanger 300 includes a first section through which the regenerated air flows between the moisture adsorber 103 and the evaporator 210.
- the evaporator 210 is connected via the second throttle 250. It may be configured to be connected to.
- the refrigerant since the refrigerant has the first restriction and the second restriction, the refrigerant pressure drops during the passage of the refrigerant through the first restriction and the passage of the second restriction, respectively. Evaporation of the refrigerant passing through the first section and condensation of the refrigerant passing through the second section are performed at an intermediate pressure between the condensation pressure of the refrigerant in the condenser and the evaporation pressure of the refrigerant in the evaporator. . Therefore, the heat exchanger acts as an economizer, and the operating coefficient (COP) of the heat pump is improved.
- COP operating coefficient
- the dehumidifier is connected to a condenser 220 via a first throttle 33 1 a (33 2 a, 33 33 a), and After passing through 3 0 and the second section 3 2 0 alternately and repeatedly, it is connected to the evaporator 2 1 0 via the corresponding second throttle 3 3 1 b (3 3 2 b, 3 3 3 c)
- a plurality of thin tube groups 5 1 (52, 5 3) configured so as to be formed, and the first throttles 3 31 a, respectively corresponding to the plurality of thin tube groups 51, 52, 53.
- a plurality of combinations of 3332a, 3333a and the second diaphragms 3311b, 3332b, 3333c may be provided.
- the first section 3 10 and the second section 3 220 have the regenerated air flowing through the sections 3 10 and 3 20 flowing opposite to each other. It is preferable to configure as follows.
- the first section 310 and the second section 320 are formed such that regenerated air flowing through the sections 310 and 320 oppose each other. At least one pair in the first section 310 and the second section 320 in the first plane PB substantially perpendicular to the flow of the regeneration air.
- a second section PC having a first section penetration section 25 1 B and a second section penetration section 252 B, and being substantially orthogonal to the flow of the regenerated air different from the first plane PB. Which has at least one pair of first section penetration portions 25 1 C and a second section penetration portion 25 2, and moves from the first surface PB to the second surface PC.
- An intermediate aperture 331 may be provided in the first embodiment.
- the heat exchange between the regenerated air flowing through each section can be similar to the counterflow heat exchange. However, the heat exchange efficiency can be increased.
- the shapes of the first surface and the second surface are typically rectangular planes.
- the second heat exchanger 340 that is disposed in the flow path of the recycled air to be circulated and exchanges heat with the recycled air and another fluid is provided. It may be provided.
- the second heat exchanger since the second heat exchanger is provided, heat exchange between the regeneration air and another fluid can be performed, and the regeneration air can be cooled or heated.
- the second heat exchanger typically cools the regeneration air.
- the second heat exchanger 340a is a second heat exchanger that connects the condenser 220 and the first heat exchanger 300 to flow the refrigerant.
- the second group of thin tubes is configured to guide the refrigerant condensed in the condenser 220 to the first heat exchanger 300;
- the regenerated air flowing between the first heat exchanger 300 and the other fluid may be configured to alternately contact the other air.
- the second heat exchanger can perform heat exchange between the regenerated air and the other fluid via the refrigerant.
- the other fluid is preferably external air.
- the excess heat of the regeneration air can be released to the outside air, which is a semi-exhaustive heat source.
- FIG. 1 is a flowchart of a dehumidifier according to a first embodiment of the present invention.
- FIG. 2 is a schematic front sectional view showing the structure of the dehumidifier shown in FIG.
- FIG. 3 is a Mollier diagram of the heat pump of the dehumidifier shown in FIG.
- FIG. 4 is a psychrometric chart explaining the operation of the dehumidifier of FIG.
- FIG. 5 is a schematic cross-sectional view illustrating the behavior of the refrigerant in the first heat exchanger and the second heat exchanger used in the embodiment of the present invention.
- FIG. 6 is a flowchart of a dehumidifying apparatus according to the second embodiment of the present invention.
- FIG. 7 is a Mollier diagram of the heat pump of the dehumidifier shown in FIG.
- FIG. 8 is a flowchart showing extracted main parts of the dehumidifier according to the third embodiment of the present invention.
- FIG. 9 is a Mollier diagram of the heat pump of the dehumidifier shown in FIG.
- FIG. 10 is a front view illustrating a heat exchanger portion of a dehumidifier according to a fourth embodiment of the present invention.
- FIG. 11 is a Mollier diagram of the heat pump of the dehumidifier shown in FIG.
- FIG. 12 is a schematic cross-sectional plan view and a side cross-sectional view of a heat exchanger suitable for use in a heat pump of a dehumidifier according to an embodiment of the present invention.
- FIG. 13 is a flow diagram showing an extracted heat exchanger part of the dehumidifier according to the fifth embodiment of the present invention.
- FIG. 14 is a Mollier diagram of the heat pump of the dehumidifier shown in FIG.
- FIG. 15 is a schematic enlarged plan view of the heat exchanger shown in FIG.
- FIG. 16 is a partially cutaway perspective view showing the structure of a typical desiccant rotor used in the dehumidifier according to the embodiment of the present invention.
- FIG. 17 is a flowchart of a conventional dehumidifying air conditioner. Explanation of reference numerals
- FIG. 1 is a flowchart of a dehumidifying device 21 according to a first embodiment of the present invention.
- the dehumidifier 21 is a dehumidifier 21 that circulates the regeneration air B to regenerate the desiccant and dehumidifies the processing air A using the desiccant.
- FIG. 2 is a schematic front sectional view of the dehumidifier 21 of FIG.
- FIG. 3 is a refrigerant Mollier diagram of the heat pump HP1 included in the dehumidifier 21 of FIG. 1, and
- FIG. 4 is a psychrometric chart of the dehumidifier 21 of FIG.
- the configuration of the dehumidifying device 21 according to the first embodiment will be described with reference to FIG.
- the dehumidifier 21 cools the regenerated air B after regenerating the desiccant to a temperature below its dew point, recovers the moisture in the regenerated air B as dew water, and dehumidifies the treated air A with the regenerated desiccant.
- the air conditioning space 101 to which the processing air A is supplied is maintained at a low humidity.
- the processing air-related equipment configuration will be described along the path of the processing air A from the air-conditioned space 101.
- the desiccant rotor 103 filled with the desiccant to reduce the humidity is arranged in the order of the path 109 and the processing air A is configured to return from the path 109 to the air-conditioned space 101.
- Each of the routes 107 to 109 connects the devices and the like described before each of the routes 107 to 109 with the devices and the like described later.
- the desiccant rotor 103 is the moisture adsorption device of the present invention.
- An evaporator 210 for recovering the water in B as dew condensation water and a path 12 9 are arranged in this order, and the regenerated air B is supplied from the path 12 9 to the second section of the heat exchanger 300.
- each of the routes 124 to 129 connects the device described before each of the routes 124 to 129 with the device described later.
- the water in the regeneration air B, which has been condensed by the evaporator 210, is collected by a drain pan 451, which is installed vertically below the evaporator 210, and the drain tank 450 Is accumulated in
- An evaporator 210 that heats and evaporates the refrigerant C with the regeneration air, a path 210, and a compressor as a pressure booster according to the present invention, which compresses the refrigerant C that evaporates and becomes a gas in the evaporator 210.
- Condensing section 2 52 for heating regenerated air B flowing through second section 320, evaporating section 2 for cooling regenerated air B flowing through first section 310 of first heat exchanger 300 51, a path 204 in which a throttle 250 is arranged in the middle, are arranged in this order, and the refrigerant C is configured to return to the evaporator 210 again.
- Each of the routes 201 to 204 connects the device described before each of the routes 201 to 204 in the above description and the device described later.
- the desiccant rotor 103 will be described later in detail with reference to FIG.
- the heat exchanger 300 is a heat exchanger that indirectly exchanges heat between the regenerated air B before and after flowing into the evaporator 210 via the refrigerant C.
- the heat exchanger 300 is located in a plurality of different planes PA, PB, PC, and PD (four planes in the drawing, but not limited thereto) which are perpendicular to the plane of the drawing and perpendicular to the flow of the regeneration air B.
- a plurality of heat exchange tubes as refrigerant passages or as thin tubes are arranged substantially in parallel. In this figure, only one tube is shown in each plane for convenience of illustration.
- the heat exchanger 300 is provided with a first section 310 flowing the regenerated air B before passing through the evaporator 210, and a second section 310 flowing the regenerated air B after passing the evaporator 210.
- Section 320 constitutes a separate rectangular parallelepiped space.
- a partition 301 and a partition 302 are provided adjacent to each other, and a heat exchange tube is provided through the two partitions 301, 302.
- the heat exchanger 300 divides one rectangular parallelepiped space by one partition wall, and a heat exchange tube as a group of thin tubes penetrates the partition wall to form a first partition and a second partition. Alternately with the parcel (See Fig. 5 and Fig. 12).
- the regenerated air B that has exited the desiccant rotor 103 is precooled by passing through the heat exchanger 340 from the right side of the figure through the path 126a, and then heat-exchanging through the path 126b. It is supplied to the first section 310 of the vessel 300 and exits through the path 127 from the left in the figure.
- the regenerated air B which has been cooled to a temperature lower than the dew point temperature and reduced in absolute humidity through the evaporator 210, passes from the left side of the figure through the path 129 to the second section 3 2 of the heat exchanger 300. It is supplied to 0 and exits from the right side of the figure through route 1 2 4.
- the heat exchange tube passes through the first section 310 and the second section 320 and the partition wall 301 and the partition wall 302 that separates the sections.
- a heat exchange tube arranged in the plane PA may be used to define the part penetrating the first compartment 310 as an evaporating section 25A (hereinafter, when it is not necessary to discuss a plurality of evaporating sections individually).
- the part penetrating through the second section 320 is referred to as the condensing section 25 A (hereinafter simply referred to as the condensing section when it is not necessary to discuss a plurality of condensing sections individually).
- the evaporating section 25 1 A and the condensing section 25 2 A are a pair of a first section penetration section and a second section penetration section, and constitute a refrigerant passage.
- the evaporating section which is a portion penetrating the first section 310, is designated as 251B.
- a portion that penetrates through the second section 320 and forms a pair of refrigerant paths with the evaporating section 251 B is referred to as a condensation section 252 B.
- a refrigerant path is also configured for the planes P C, similarly to the plane P B.
- the evaporating section 25 1 A and the condensing section 25 2 A make a pair, and are configured as an integrated path by one tube. Therefore, in combination with the fact that the first section 310 and the second section 320 are provided adjacent to each other via the two partitions 301, 302, the heat exchanger 30 0 can be formed as a small compact as a whole.
- the evaporation sections as the first section penetrations are arranged in the order of 251A, 251B, 251C
- Condensation sections as section penetrations are also arranged in the order of 252A, 252B, 252C ⁇ 'from the right in the figure.
- the end of the evaporating section 25 1 A (the end opposite to the bulkhead 301) and the end of the evaporating section 25 1B (the end opposite the bulkhead 301) ) Is a U tube One tube).
- the end of the condensing section 25B and the end of the condensing section 25C are similarly connected by a U-tube.
- the refrigerant C flowing in one direction as a whole from the condensing section 25 2 A to the evaporating section 25 1 A is guided to the evaporating section 25 1 B by the U-tube, and flows therefrom to the condensing section 25 2 B.
- the condensing section is configured to flow to the 25 C through a U-tube.
- the refrigerant path including the evaporating section and the condensing section alternately and repeatedly passes through the first section 310 and the second section 320.
- the refrigerant path forms a meandering group of small tubes.
- the tubules pass through the first section 310 and the second section 320 while meandering, and alternately contact the high-temperature regeneration air B and the low-temperature regeneration air B.
- the refrigerant from the throttle 330 is first guided to the condensing section 250 A, but it may be configured to be first guided to the evaporating section 251 A.
- the end of the condensing section 25 A (the end opposite the partition wall 302) and the end of the condensing section 25 B (the end opposite the partition wall 302) Are connected by a U-tube, and the end of the evaporating section 25 1 B and the end of the evaporating section 25 1 C are similarly connected by a U-tube.
- a refrigerant gas C compressed by a refrigerant compressor 260 is guided to a condenser 220 via a refrigerant gas pipe 202 connected to a discharge port of the compressor 260.
- the refrigerant gas C compressed by the compressor 260 is cooled and condensed by the regeneration air B serving as cooling air immediately before flowing into the desiccant rotor 103, and the refrigerant C heats the regeneration air B.
- the refrigerant outlet of the condenser 220 is connected to the inlet of the condensing section 250 A of the heat exchanger 300 by the refrigerant path 203, and in the middle of the refrigerant path 203, the condensing section 205.
- a throttle 330 is provided near the entrance of 2A.
- the liquid refrigerant C that has exited the condenser 220 is depressurized by the throttle 330, expands, and a portion of the liquid refrigerant C evaporates (flashes).
- the refrigerant C which is a mixture of the liquid and the gas, reaches the condensing section 250A, where the liquid refrigerant C flows so as to wet the inner wall of the tube of the condensing section 250A, and from the evaporator 210.
- the coolant cooled and flushed by the cooled regeneration air B immediately after flowing out condenses.
- the regeneration air B flowing through the second section 320 Due to the condensation of the refrigerant, the regeneration air B flowing through the second section 320, The regenerated air B that has been cooled and dehumidified in the evaporator 210 and has a lower temperature than before flowing into the evaporator 210 is heated (preheated).
- the condensing section 25 2 A and the evaporating section 25 1 A are a series of tubes. That is, the condensed refrigerant liquid C (and also the non-condensed refrigerant liquid C) flows into the evaporating section 25A because it is configured as an integrated path. Then, the regenerated air B flows out of the desiccant rotor 103, is heated and evaporated by the regenerated air B cooled to some extent in the heat exchanger 340, and the regenerated air B flowing through the first section 310 is scattered. Cool (pre-cool). The regeneration air B is the regeneration air B before flowing into the evaporator 210.
- the heat exchanger 300 is provided in the first plane PA with the refrigerant passing through the first section 310 and the evaporating section and the refrigerant passing through the second section 320.
- a refrigerant section having at least one condensing section (at least one pair, for example, 25A and 25A) and passing through a second compartment 320 in the second plane PB. It has a condensing section and an evaporating section (at least one pair, e.g., 25B and 25B), which is a refrigerant path through the first compartment 310.
- the outlet side of the last condensing section 2 52 D of the heat exchanger 300 is connected to the evaporator 210 by a refrigerant liquid pipe 204, and an expansion valve as a throttle is provided in the refrigerant pipe 204. 250 are installed.
- the refrigerant liquid C condensed in the condensing section 255 is decompressed and expanded by the throttle 250 to lower the temperature, enters the evaporator 210 and evaporates, and cools the regenerated air B by the heat of evaporation.
- the throttles 330 and 250 for example, orifices, capillary tubes, expansion valves and the like are used.
- the refrigerant C evaporated and gasified in the evaporator 210 is guided to the suction side of the refrigerant compressor 260 through the path 201, and the above cycle is repeated.
- the heat pump HP1 pumps heat from the low-temperature regeneration air, which is a low heat source, to the high-temperature regeneration air, which is a high heat source.
- the dehumidifier 21 uses the heat pump HP 1 to simultaneously regenerate the desiccant and remove moisture from the regenerated air, and also preheats the regenerated air B before regeneration and regenerates the regenerated air B after regeneration. Since the pre-cooling is performed using the internal working medium, the equipment is simple, and most of the cooling capacity of the heat pump can be used to condense the moisture in the air, so the dehumidifying capacity is high.
- an air / air heat exchanger 300 is installed before and after the evaporator 210 to perform pre-cooling and reheating (pre-heating) of the regenerated air B to reduce the sensible heat ratio and cool down to the dew point. Was reduced.
- the dehumidifier 21 has a high dehumidifying capacity and, in addition, recovers heat for cooling to the dew point and can use it as heat for heating the regenerated air. be able to. Therefore, the amount of heat required is smaller than the amount of heat required by the conventional electric heater, and the heat pump HP1 has high energy efficiency and consumes less power.
- the equipment constituting the device is housed in a cabinet 700.
- the cabinet 700 is formed as a rectangular parallelepiped housing made of, for example, a thin steel plate, and has an upper region 700 A arranged vertically above and below by a horizontal plane-shaped partition plate 700. It is hermetically sealed in the lower area 700B.
- the upper area 700 A is a processing air chamber 702 through which the processing air A flows from the left end to the right end in the drawing
- the lower area 700 B is a regeneration air chamber 703 mainly.
- the regeneration air B circulates in the regeneration air chamber 703 as described later.
- the partition plate 700 for example, a thin steel plate constituting the cabinet 700 may be used.
- the intake port 104 opens at the top in the vertical direction of the left side 704 A of the cabinet 704 in the figure, and the intake port 104 is the processing air A for the air-conditioned space 101 (see Fig. 1). To inhale.
- the intake port 104 is an opening of the processing air chamber 702, and the sucked processing air A flows through the processing air chamber 702.
- a filter 501 is provided near the intake port 104 in the processing air chamber 702 so as to prevent dust in the air-conditioned space 101 from being brought into the apparatus.
- a blower 102 is installed inside the filter 501, and the processing air A flowing from the intake port 104 through the filter 501 into the processing air chamber 702 is blower 10 2 sucked.
- a path 107 is formed between the intake port 104 and the blower 102.
- the processing air A flows through the processing air chamber 702 by the blower 102.
- the process air A discharged from the blower 102 flows through the path 108, flows into the upper half of the desiccant rotor 103 from the horizontal direction, and is removed by the desiccant of the desiccant rotor 103.
- Processed air A that has flowed horizontally from the upper half of the desiccant rotor 103 passes through the path 109 and opens at the top of the cabinet 704 on the right side in the figure on the right side of the cabinet 704 B in the vertical direction.
- the air exits the processing air chamber 720 ie, exits the cabinet 700 from the discharge port 110, and returns to the air-conditioned space 101 to be supplied with air.
- the desiccant rotor 103 is arranged so that the rotation axis AX is directed in the horizontal direction and passes through an opening 706 formed in the partition plate 701, and the upper half of the semicircular shape is the processing air chamber 702. In addition, the lower half of the semicircular shape is disposed in an upper section 703 A of the regeneration air chamber 703 described later.
- An electric motor 105 serving as a driving machine is arranged near the desiccant rotor 103 in an area 703 A, which will be described later, of the regeneration air chamber 703 with its rotating shaft being horizontal.
- the electric motor 105 and the desiccant rotor 103 are connected via a chain 131, and the rotation of the electric motor 105 is transmitted to the desiccant rotor 103, and the desiccant rotor 103 is 15- 2 0 hr-rotate at 1 speed. Since the desiccant rotor 103 is arranged with the rotation axis AX oriented in the horizontal direction, the horizontal length of the cabinet 700 can be made short and compact.
- the height of the processing air chamber 702 is formed slightly larger than the radius of the desiccant rotor 103, and the height of the regeneration air chamber 703 is formed slightly smaller than twice the radius of the desiccant rotor 103. ing.
- a horizontal plane-shaped partition plate 707 is provided, separated from the partition plate 701 by a distance slightly larger than the radius of the desiccant rotor 103, to the lower side.
- the air chamber 703 is divided into two vertical sections 703 A and 703 B by a partition plate 707. Openings 705 A, B are formed at both ends of the partition plate 707, and pass through the openings 705 A, 705 B, and the upper and lower areas 703 A, 703 B Is formed so that the regenerated air B circulates.
- a filter 502 is installed on the right side of the upper area 703 A of the regeneration air chamber 703 in the figure, and passes through the opening 705 B on the right side of the figure, and the lower area 70 0 3 Remove the dust from the regeneration air B that rises from B and turns in the horizontal direction.
- a condenser 220 having a heat exchange tube formed in a coil shape is installed on the left side of the filter 502 in the figure. The regenerated air B after passing through the filter 502 passes through the condenser 220 and is heated.
- the regeneration air B passing through the condenser 220 and passing through the path 125 flows into the lower half of the desiccant rotor 103 from the horizontal direction to regenerate the desiccant.
- the regeneration air B that has passed through the heat exchanger 340 and passed through the path 126 b flows into the first section 310 of the heat exchanger 300 and is precooled. Outside air as another fluid is introduced into the heat exchanger 340 via a duct (not shown). When the cabinet 700 is not installed in the air-conditioned space 101, the external air duct used in the heat exchanger 340 is unnecessary.
- the air in the environment where the cabinet 700 is installed is used as it is as a fluid for exchanging heat with the regenerated air.
- cooling water may be used for the heat exchanger 340 instead of outside air. In that case, connect the cooling water supply pipe and the return pipe to the heat exchanger 340.
- the heat exchanger 300 passes through the opening 708 formed in the partition plate 707 and is housed in the upper area 703A and the lower area 703B of the regeneration air chamber 703.
- the first section 310 of the heat exchanger 300 is stored in the upper section 703A
- the second section 320 of the heat exchanger 300 is stored in the lower section 703B. Have been.
- the regenerated air B flowing out of the first section 310 of the heat exchanger 300 is sucked into a blower 140 that circulates the regenerated air B in the regenerated air chamber 703 through a path 127. .
- the regenerated air B discharged from the blower 140 passes through an extremely short path 128, passes through an evaporator 210 having a coil-shaped heat exchange tube, is cooled, and is cooled. While flowing through 9, change the direction of the flow to just below and pass through the opening 705 A on the left side in the figure.
- the regeneration air B passing through the opening 705A changes the flow direction to the horizontal direction, flows horizontally in the lower area 703B of the regeneration air chamber 703, and passes through the heat exchanger 300.
- the drain tank 450 and the compressor 260 are disposed so as to avoid the regeneration air chamber 703 on the front side in the horizontal direction in the figure.
- the regenerated air B that has flowed out of the second section 320 of the heat exchanger 300 flows along the path 124, changes the direction of the flow to just above, and passes through the opening 705B on the right side in the figure. Then, the direction of the flow is changed to the horizontal direction, reaches the filter 502, and thereafter the same flow is repeatedly circulated.
- a compressor 260 and a drain tank 450 are arranged below the partition plate 707 so as to avoid the area 703 B below the regeneration air chamber 703.
- the compressor 260 is located almost directly below the desiccant rotor 103 when viewed from the front in the figure, and the drain tank 450 is located almost directly below the evaporator 210.
- Routes 201 to 204 are arranged by connecting the devices as shown in FIG.
- the processing air A is arranged to flow in the horizontal direction, and the regeneration air B is mainly
- the equipment has been described as being arranged so that it flows and circulates slightly in the vertical direction.However, the processing air A is arranged so as to flow in the vertical direction, and the regeneration air B flows mainly in the vertical direction, and the water squares slightly.
- the devices may be arranged so as to flow and circulate in a direction.
- FIG. 3 is a Mollier diagram when HF C 134a is used as the refrigerant C. See Figure 1 for equipment.
- the horizontal axis is enthalpy h (kj / kg), and the vertical axis is pressure p (MPa).
- the refrigerant C suitable for the heat pump and the dehumidifier 21 (see FIG. 1) of the present invention there are HF C407C and HFC410A. In these refrigerants C, the working pressure region shifts to a higher pressure side than HFC 134a.
- the point a is the state of the refrigerant outlet of the evaporator 210 in FIG. 1 and is in the state of saturated gas.
- the pressure is 0.30MPa
- the temperature is 1 ° C
- the enthalpy is 399.2 kJ / kg.
- the state where the gas is sucked and compressed by the compressor 260, that is, the state at the discharge port of the compressor 260 is indicated by a point b. In this state, the pressure is 1.89 MPa, and the state is a superheated gas.
- This refrigerant gas C is cooled in the condenser 220 and reaches a point c on the Mollier diagram.
- This refrigerant liquid C is decompressed by the throttle 330 and flows into the condensation section 252 A of the heat exchanger 300.
- the pressure is a medium pressure in the present invention, and in this embodiment, the pressure is a value intermediate between 0.301 ⁇ & 1.89 MPa. In this example, the saturation pressure is 15 ° C.
- a part of the liquid is evaporated and the liquid and the gas are mixed.
- the refrigerant liquid C condenses under the intermediate pressure, and reaches a point 1 on the saturated liquid line at the same pressure.
- the refrigerant C in the state indicated by the point f1 flows into the evaporating section 25A.
- the refrigerant C takes heat from the relatively hot regenerated air B flowing in the first section 310, evaporates itself, flows further into the evaporating section 25 1 B and saturates It reaches a point gl between the liquid line and the saturated gas line.
- a part of the liquid has evaporated, but a considerable amount of the refrigerant liquid C remains.
- the refrigerant C in the state of the point g1 flows into the condensing section 2 52B and further flows into 252C. Then, the liquid phase is cooled and the liquid phase is increased to reach the point ⁇ 2 on the saturated liquid line.
- the refrigerant C here evaporates in the liquid phase to reach the point g 2.
- refrigerant C condenses in the next condensing section 25 2 D to reach point f 3 on the saturated liquid line. In this way, the refrigerant C exchanges heat between the low-temperature regeneration air and the high-temperature regeneration air while repeatedly condensing and evaporating.
- the refrigerant C in the state of the condensed point f 3 is guided to the expansion valve 250.
- Point f 3 is on the saturated liquid line in the Mollier diagram.
- the temperature is 15 ° C and the enthalpy is 20.5 kjZkg.
- the refrigerant liquid C at the point f3 is reduced in pressure by the throttle 250 to 0.3 OMPa which is a saturation pressure at a temperature of 1 ° C, and reaches the point j.
- the refrigerant C at this point flows into the evaporator 210 as a mixture of the refrigerant liquid C at 1 ° C and gas, where it takes heat from the treated air A, evaporates, and evaporates to a point a on the Mollier diagram.
- the saturated gas in the state described above is sucked into the regenerative compressor 260, and the above cycle is repeated.
- the refrigerant in the state e is not condensed in the evaporating section 251, but is condensed in the condensing section 252 as in the present embodiment, the refrigerant approaches a wet state. Therefore, when the capacity control is performed, the amount of the gas-phase refrigerant passing through the throttle 250 is reduced, and the refrigeration effect can be maintained high.
- the refrigerant C evaporates the change in the state of condensation, as in the condensing section 252, from point e to point f1, or from g1 to f2.
- the state of evaporation changes from point f1 to point g1, or from point f2 to g2, as it is condensation heat transfer and evaporation heat transfer. Very high heat transfer coefficient.
- a compression heat pump HP 1 including a compressor 260, a condenser 220, a throttle 330, 250 and an evaporator 210
- the heat exchanger 30 ° is not provided
- the refrigerant enthalpy at the evaporator 210 inlet is reduced, and the refrigerant refrigeration effect per unit flow rate is high, so the dehumidification effect and energy efficiency are high. It will be.
- the dehumidifier 21 including the heat pump HP1 will be described with reference to the psychrometric chart of FIG. 4 and the configuration as appropriate with reference to FIG.
- the state of air in each part is indicated by the alphabet symbol KLPR and the like. This symbol corresponds to the letter circled in the flow diagram in Figure 1.
- this diagram can be applied to the dehumidifiers of the second and third embodiments described later as the wet psychrometric chart.
- the processing air A (state K) from the air conditioning space 101 is sucked into the blower 102 through the processing air path 107, is further discharged from the blower 102, and is sent to the desiccant rotor 103 through the path 108.
- the treated air A whose moisture has been adsorbed and dried by the desiccant rotor 103 lowers the absolute humidity to 2 g / kg DA and raises the dry bulb temperature (state).
- the treated air A then returns to the conditioned space 101 via path 109.
- DA indicates dry air (DryAir).
- the regenerated air B (state P) having an absolute humidity of 5 gZk gDA and a dry bulb temperature of 5 ° C exiting the evaporator 210 is sent to the second compartment 320 of the heat exchanger 300 through the path 129, where In the condensing section 252, it is heated to a certain extent by the refrigerant C condensed, and the dry bulb temperature is raised while maintaining the absolute humidity (temperature between 5 ° C and 60 ° C) (state R).
- This can be referred to as pre-heating, as it is pre-heating before heating in condenser 220.
- Preheated regeneration air B is introduced into condenser 220 via path 124.
- the regeneration air B is heated by the condenser 220, and further raises the dry bulb temperature to 60 ° C while maintaining the absolute humidity constant (state T).
- the regenerated air B is further fed into the desiccant rotor 103 through the path 125, where it takes water from the desiccant (not shown in FIG. 1) in the drying element and regenerates it. Raise to 10 g / kg DA and lower the dry-bulb temperature by desiccant hydration and heat removal ('State U a)
- the regenerated air B that has exited the desiccant rotor 103 is sent to the heat exchanger 340 through the path 126a, and the dry bulb temperature is lowered while maintaining the absolute humidity constant (state Ub).
- the regenerated air B exiting the heat exchanger 340 is sent to the first section 310 of the heat exchanger 300 through the path 126b, where it is cooled to a certain extent by the refrigerant C that evaporates in the evaporating section 251 and has a constant absolute humidity. Reduce the dry bulb temperature as it is (State V). This is pre-cooling before the evaporator 210 cools to a temperature below the dew point, so it can be called pre-cooling. Rebirth Air B is sucked by the blower 140 through the path 127 and is discharged to the path 128.
- the discharged regenerated air B is sent to the evaporator 210 through the path 128, is dehumidified and cooled to the dew point temperature or lower by the evaporator 210, reduces the absolute humidity to 5 g / kg DA, and is dried. Reduce bulb temperature to 5 ° C (state P).
- the regenerated air B exiting the evaporator 210 repeats the same cycle.
- the regeneration air B is precooled by evaporating the refrigerant C in the evaporating section 251, and the regeneration air B is heated by condensing the refrigerant C in the condensing section 250.
- the refrigerant C evaporated in the evaporation section 25 1 is condensed in the condensing section 25 2.
- the heat exchange between the regenerated air B before and after being cooled by the evaporator 210 is indirectly performed by the evaporation and condensation of the same refrigerant C.
- the amount of heat ⁇ ⁇ ⁇ that heats the regenerated air in the second section 320 is heating by utilizing waste heat, and the evaporator 210
- the amount of heat A i that cools the regenerated air in step 2 is the cooling and dehumidifying effect, and is the heat recovery power S, ⁇ by the heat exchanger 300 as an economizer.
- the heat amount A Q 1 is taken and the regeneration air B is cooled.
- the regenerated air B Since the regenerated air B is cooled to some extent by the heat exchanger 340 and then flows into the heat exchanger 300, the temperature of the regenerated air B flowing into the evaporator 210 decreases and the dew point temperature increases. , The heat pump's dehumidifying capacity per refrigeration effect increases. Also, the amount of heat released as a whole when the gas phase water in the air-conditioned space is converted into a liquid phase and stored in the tank 450, and the driving power of the compressor 260, which is not shown in FIG. The amount of heat can be discharged from the dehumidification system to the outside through the heat exchanger 340.
- the refrigerant C which has been decompressed by the throttle 330 and a part of the refrigerant liquid has expanded to become a mixture of the liquid phase and the gas phase, flows into the condensing section 252A.
- the refrigerant C preheats the regenerated air B while flowing through the condensing section 25 A, and itself is deprived of heat and flows into the evaporating section 25 A while reducing the gas phase.
- the evaporating section 25A cools the regenerated air B, which has a higher temperature than the regenerated air B in the condensing section 25A, and receives heat to evaporate the liquid-phase refrigerant C while evaporating. Enter section 2 5 1 B. While flowing through the evaporating section 25 1 B, the refrigerant C is further given heat from the high-temperature regeneration air B to further evaporate the liquid-phase refrigerant C. And the next condensation section 2 5? Flow into B.
- the refrigerant C undergoes a phase change between a gas phase and a liquid phase, Flows through. In this way, heat is exchanged between the regenerated air B before being cooled by the evaporator 210 and the regenerated air B cooled by the evaporator 210 to reduce the absolute humidity.
- the heat exchanger 300 is used as a pre-cooling / pre-heating heat exchanger, and the working fluid of the heat exchanger 300 and the working fluid (that is, the refrigerant) of the heat pump HP 1 are the same. Since the refrigerant charging process can be used in common, manufacturing costs and maintenance costs are low. In addition, a pre-cooling-pre-heating heat exchanger can be manufactured as a single unit. In addition, since the refrigerant of the working fluid flows in one direction in the refrigerant path as the refrigerant of the heat pump, it does not require the internal wick of the heat pipe and produces a normal air-refrigerant heat exchanger coil with no internal wick. Manufacturing cost is low because it can be manufactured with equipment.
- the second embodiment will be described with reference to FIG.
- the difference from the first embodiment is that a heat exchanger 340a is used instead of the heat exchanger 340.
- the heat exchanger 340a has a structure similar to that of the heat exchanger 300.
- the heat exchanger 340a consists of an evaporator section 341A, 341B and a condensing section 342A,
- the evaporating sections 34 1 A and 34 1 B correspond to the evaporating sections 25 1 A and 25 1 B of the heat exchanger 300, and the condensing sections 34 2 A and 34 2 B Exchanger 3 0
- the evaporating section is disposed through the first section 344, and the condensing section is disposed through the second section 344.
- the first parcel 3 4 3 is the desiccant center 1 0
- the regenerated air B passing through the desiccant rotor 103 is introduced into the first section of the heat exchanger 3 4 0 a. After passing through 343, it flows into the first section 310 of the heat exchanger 300.
- the second section 344 of the heat exchanger 340a is configured so that the outside air passes through the blower 144.
- a throttle 336 is arranged in the refrigerant pipe 203 flowing into the condensing section 3442A.
- the heat exchanger 340a When viewed along the flow of the refrigerant, the heat exchanger 340a is inserted and disposed in the refrigerant pipe 203 of the first embodiment.
- the refrigerant C passes through the condensing section 342 A, the evaporating section 341 A, the evaporating section 341 B, and the condensing section 342 B, and reaches the throttle 340.
- it is the heat exchanger 3 that transfers heat from the regeneration air B passing through the first compartment 344 to the outside air passing through the second compartment 344 by condensation and evaporation of the refrigerant. It is similar to the case of 0 0.
- the operation of the heat pump HP2 will be described with reference to FIG.
- FIG. 7 is a Mollier diagram in the case where FC134a is used as the refrigerant C, similarly to FIG. The description that overlaps with FIG. 3
- points a, b, c, and d are the same as those in FIG.
- the refrigerant liquid C in the state at the point d is decompressed by the throttle 3336 and flows into the condensing section 342A of the heat exchanger 340a.
- the pressure is an intermediate pressure of the present invention, and is a value intermediate between 0.30 MPa and 1.89 MPa in this embodiment. In this example, the pressure is somewhat higher than the saturation pressure at a temperature of 13 ° C.
- a part of the liquid is evaporated and the liquid and the gas are mixed.
- the condensing section 342 A the refrigerant liquid C condenses under the intermediate pressure and reaches a point f 1 on the saturated liquid line at the same pressure.
- the refrigerant C in the state indicated by the point f1 flows into the evaporating section 341A.
- the refrigerant C deprives the relatively hot regenerated air B flowing in the first section 34 43 of heat, evaporates itself and further flows into the evaporating section 34 1 B,
- the point g 1 is located between the saturated liquid line and the saturated gas line. Here, a part of the liquid is evaporated, but the refrigerant liquid C remains considerably.
- the refrigerant C in the state of the point gl flows into the condensing section 342 B, is cooled and increases the liquid phase, and reaches the point f2 on the saturated liquid line.
- the liquid refrigerant C is decompressed by the throttle 330 and flows into the condensing section 255A of the heat exchanger 300.
- the subsequent operation is the same as that described with reference to FIG. However, the signs of f1, g1, ⁇ 2, g2, and f3 in FIG. 3 are changed to f3, g3, f4, g4, and ⁇ 5, respectively. Further, as a result of being efficiently cooled by the heat exchanger 340a, the operating temperature of the heat exchanger 340 has been slightly reduced from 15 to 13 ° C.
- the heat exchanger 340a utilizing the condensation heat transfer and the evaporation heat transfer is provided, the cooling of the regenerated air B can be achieved with a high heat transfer coefficient. Further, the refrigerating effect of the refrigerant can be further enhanced.
- a third embodiment of the present invention will be described with reference to FIGS.
- the difference between this embodiment and the first embodiment shown in FIG. 1 is that the refrigerant is first introduced into the evaporating section 251A from the throttle 33 by the heat exchanger 300b. That the transition from plane PA to plane PB takes place between condensing sections 25 2 A and 25 2 B (between other planes).
- 3 3 1 The plane PE is added, the plane PE is added, the plane PB and the plane PC are evaporated between the evaporation sections, and the plane PD and the plane PE are evaporated between the evaporation sections. , 332 are provided.
- the end of the evaporating section 25 1 B in the plane PB and the end of the evaporating section 25 1 C in the plane PC are connected via the throttle 331, and the plane PD
- the end of the evaporating section 25 1 D in the inside and the end of the evaporating section 25 1 E in the plane PE are connected via a throttle 33 2.
- the other parts are the same as those shown in FIG. 1 and are not shown.
- the major change is that apertures 331 and 332 are provided between the planes.
- the other point is that the refrigerant is first flowed into the evaporator section 251A from the throttle 330, so that the evaporation and condensation in the heat exchanger 300b as a whole are closer to the gas phase. There is no significant difference in operation except for.
- the plane may be further increased than the PE, and in that case, the aperture may be increased accordingly.
- the refrigerant C introduced into the evaporating section 25 1 A partially evaporates in the evaporating section 25 1 A, becomes moist, and flows into the condensing section 25 2 A. .
- the air then turns in the U-tube and enters the condensing section 25 2 B and the evaporating section 25 1 B.
- the pressure is reduced by the throttle 331, and flows into the evaporating section 251C in the plane PC.
- it evaporates further and flows into the condensing section 25 2 C.
- it turns in the U-tube and flows into the condensing section 252D, and is further condensed and flows into the evaporating section 251D.
- a part of the refrigerant C evaporates and reaches the throttle 332.
- the pressure is reduced and flows into the evaporating section 25 1 E in the plane PE and then into the condensing section 25 2 E.
- the refrigerant C that has sufficiently condensed here travels to the path 204 and the expansion valve 250.
- the evaporating pressure in the evaporating sections 25 1 A and 25 1 B, and thus the condensing pressure in the condensing sections 25 2 A and 25 2 B that is, the first intermediate pressure, or the evaporating section 25 1 C, 25 1 D, condensation section 25 2 C, 25 2 D
- the pressure in the second intermediate pressure, ie, the temperature of the regeneration air B before entering the evaporator 210, and the evaporator 210 It is determined by the temperature of the regenerated air B after entering, cooling and exiting.
- the heat exchanger 300 shown in FIG. 1 or the heat exchanger 300 b shown in FIG. 8 utilizes the evaporative heat transfer and the condensed heat transfer, and therefore has a very excellent heat transfer coefficient.
- heat exchanger 300b Since the heat exchange between the raw air B is performed in a counter-flow type, as described later, the heat exchange efficiency is extremely high.
- the refrigerant C is forced to flow in almost one direction as a whole in the refrigerant path from the evaporating section 251 to the condensing section 252 and from the condensing section 252 to the evaporating section 251. High heat exchange efficiency between regeneration air B and regeneration air B with low temperature.
- the flow as a whole generally in one direction means that, for example, a turbulent flow may locally flow backward, but also a pressure wave is generated due to the generation of a bubble or an instantaneous interruption, and the refrigerant C flows in the flow direction. Even if it vibrates, it means that it flows in one direction in the refrigerant path as a whole.
- refrigerant C is forcibly flowed in one direction at a pressure increased by compressor 260.
- the heat exchange efficiency ⁇ is defined as TP1, the inlet temperature of the heat exchanger for the high-temperature fluid, T for the outlet temperature, TC1, the inlet temperature of the heat exchanger for the low-temperature fluid, and TC2 for the outlet temperature.
- the refrigerant C in the state of the point e that has flowed into the evaporating section 25 1 A of the heat exchanger 300b has a part of the liquid evaporated at the first intermediate pressure and the liquid and the gas. Are in a mixed state.
- the refrigerant C further evaporates in the evaporating section 251 A, and reaches a point f 1 in the Mollier diagram that approaches the saturated gas line in the wet area.
- Refrigerant C in this state enters condensing section 25 2 A, where it is condensed and reversed in U-tube and enters condensing section 25 2 B, where it is further condensed to a point g in the wet region but close to the saturated liquid line g Reaches one.
- the evaporating section 25 1 B and in the wet area heads in the direction of the saturated gas line to the point hia. Up to this point, the change is almost at the first intermediate pressure.
- the refrigerant C in the state of the point h 1 a is reduced in pressure through the throttle 331 to reach the point h 1 b at the second intermediate pressure. That is, the refrigerant flows from the evaporating section 25 1 B, which is the refrigerant path in the plane PB, to the evaporating section 25 C, which is the refrigerant path of the plane PC, via the throttle 331, through the throttle 331.
- the refrigerant C further evaporates at the second intermediate pressure in the evaporating section 25 1 C to reach the point f 2.
- the pressure is reduced by the intermediate throttle 332.After that, the pressure becomes the third intermediate pressure, and the refrigerant C passes through the evaporating section 25 1 E, the condensing section 25 2 E, and the refrigerant path. Leads to a point g 3 on the Mollier diagram, which corresponds to point ⁇ 3 in FIG. This point is on the saturated liquid line in the Mollier diagram.
- the temperature is 11 ° C and the enthalpy is 25.0 kJ / kg.
- the refrigerant liquid C at the point g 3 is reduced to 0.30 MPa, which is the saturation pressure at a temperature of 1 ° C, with the throttle 250 as in the case of FIG. Reaches the evaporator 210 as a mixture of the refrigerant liquid C and the gas, where it removes heat from the regenerated air B and evaporates to become saturated gas at the point a on the Mollier diagram. The above cycle is repeated.
- the refrigerant C alternately changes the state of evaporation and condensation, and the heat transfer coefficient is very high because the heat transfer is evaporation heat and condensation heat. This is the same as the heat exchanger 300 of the first embodiment.
- the regenerated air B before being cooled by the evaporator 210 is supplied to the evaporator sections 251A, 251B, 251C, 25 in the first section 310.
- the regenerated air B, cooled by the evaporator 210 is condensed in the second section 320 in the order of the condensing sections 25E, 25D, 25C, 25B, and 25A.
- Exchange heat That is, the temperature gradient of the regeneration air B and the temperature gradient of the condensation section 252 are in the same direction.
- FIG. 10 shows a flowchart of a dehumidifying device 23 according to the fourth embodiment.
- the throttles 33 1 and 3 32 It is provided on the 25 2 side. So The other configuration is the same as that of the second embodiment described with reference to FIG.
- FIG. 11 is a Mollier diagram of the heat pump HP 4 shown in FIG. Unlike Fig. 9, the pressure is reduced during the condensation process at the intermediate pressure.
- the aperture 331 reduces the pressure from the point g 1 a to the point g 1 b
- the aperture 332 reduces the pressure from the point g 2 a to the point g 2 b.
- the point that the heat exchange between the regenerated air B before and after being cooled by the evaporator 210 is countercurrent is the same as in the embodiment of FIG.
- Restrictors may be installed on both sides of the evaporating section and the condensing section, as shown in Fig. 8 and Fig. 10. With such a configuration, there is a throttle every time the refrigerant moves from one plane to the next plane, and the evaporation temperature / condensation temperature differs from plane to plane, so that the flow of the regenerated air that exchanges heat is completely countercurrent. Get closer.
- the drain pan 451 is not limited to the evaporator 210, but may be provided so as to provide power below the heat exchangers 300, 300b, and 300c. In particular, it is preferable to be provided below the first section 310. In the first section 310 of the heat exchangers 300, 300b, and 300c, the regeneration air B is pre-cooled, but some moisture may condense here.
- (A) is a plan view of the flow direction of the low-temperature and high-temperature regeneration air B
- (b) is a side view of the low-temperature and high-temperature regeneration air at right angles to the flow.
- (a) is a view taken in the direction of arrows A—A in (b).
- the regenerated air B having a high temperature flows through the section 310 from the near side of the paper to the front
- the regenerated air B having a low temperature flows through the section 320 from the front to the near side.
- the tubes are arranged in eight rows in four planes PA, PB, PC, and PD, respectively, which are orthogonal to the flow of the low-temperature and high-temperature regeneration air B. That is, they are arranged in 4 rows and 8 columns along the flow of the regeneration air B.
- a plane PE (not shown) may be provided below the plane PD, and eight more rows of tubes may be arranged in the plane PE.
- FIG. 1, FIG. 5, FIG. 6, FIG. 8 and FIG. 10 for convenience, the heat exchange tubes in each plane PA, PB, PC, PD are described as having one row and one column, but typically, Thus, each row contains a plurality of tube rows. In this way, the tubes constitute a group of tubules.
- An intermediate stop 331 is provided at the point where the first plane PA moves to the next plane PB, a middle stop 332 (not shown) is provided at the point where the plane PB is transferred to the plane PC, and a middle stop 332 is provided at the point where the plane PC is transferred to the plane PD.
- An aperture 3 3 3 is provided.
- one stop is provided at a position where one plane moves to the next plane.
- a tube row belonging to PA may be formed of a plurality of layers.
- An intermediate stop is provided at a position where each layer moves to the next layer.
- the planes before and after the intermediate stop are referred to as a first plane and a second plane.
- heat exchangers As shown in Fig. 12 in parallel with the flow of the low-temperature and high-temperature regeneration air, They may be arranged in series. Furthermore, for example, in the Mollier diagram shown in Fig. 11, the repetition of evaporation and condensation of refrigerant C is established as a cycle even if the refrigerant enters the supercooling region beyond the saturated liquid line, but it is heat exchange between regenerated air In consideration of the above, it is preferable that the phase change of the refrigerant c is performed in the wet region. Therefore, in the heat exchanger 300d shown in Fig.
- the heat transfer area of the first evaporator section connected to the throttle 330 should be larger than the heat transfer area of the subsequent evaporator section. I like it. Also, since the refrigerant C flowing into the throttle 250 is preferably in a saturated or supercooled region, the heat transfer area of the condensing section connected to the throttle 250 is reduced by the transfer of the condensing section before it. It is preferable to configure the heat area larger than the heat area.
- This heat exchanger is inexpensive and is economical when used in place of expensive heat pipes. Unlike heat pipes, the working fluid can be the same as that of a heat pump, so there is no need for maintenance.
- FIG. 13 is a flow diagram schematically showing a flow in the dehumidifying device in the fifth embodiment
- FIG. 14 is a refrigerant Mollier diagram of the heat pump HP5 included in the dehumidifying device of FIG.
- FIG. 3 shows only the heat exchanger 300 e and the path of the refrigerant and air around the heat exchanger 300 e, and the others are not shown.
- the heat exchanger 300b in the third embodiment in FIG. 8 is replaced with a heat exchanger 300e.
- members or elements having the same functions or functions as the members or elements in the third embodiment are denoted by the same reference numerals, and parts that are not particularly described are the same as those in the third embodiment. .
- the refrigerant path is branched into a plurality of rows (three rows in FIG. 13) on the downstream side of the condenser 220, and the branched refrigerant paths 51 to 53 are formed. This is different from the other embodiments in the point.
- the branch refrigerant paths 51 to 53 join one refrigerant path 204 on the upstream side of the evaporator 210. That is, a plurality of condensers between the condenser 220 and the evaporator 210 A branch refrigerant path that branches into rows is provided, and a first heat exchange means and a second heat exchange means are provided in the branch refrigerant path.
- the dehumidifier of the present embodiment is connected to the condenser 220 through the first throttle 3311a (3332a, 3333a), Of the evaporator 2 through the corresponding second restrictor 3'3 1b (3 3 2b, 3 3 3c)
- a plurality of thin tube groups 5 1 (5 2, 5 3) configured to be connected to 10
- the first diaphragm 3 corresponding to each of the plurality of thin tube groups 5 1, 5 2, 5 3
- a plurality of combinations of 31a, 3332a, 3333a and the second diaphragms 3311b, 3332b, 3333c are provided. .
- the estuary refrigerant passages 51 to 53 include the first heat exchange section (first section) 310 and the second heat exchange section (second section) 320 of the heat exchanger 300 e. Are repeatedly and alternately penetrated. Also, in each of the branch refrigerant paths 5 :! to 53, throttles 331a to 333a are arranged on the upstream side of the first heat exchange section 310, respectively. Restrictors 3311b to 3333b are arranged downstream of the part 320. As the throttles 331a to 3333b, for example, an orifice, a capillary tube, an expansion valve, or the like can be used.
- first section 310 and the second section 320 are configured such that the regenerated air flowing through the sections 310, 320 flows opposite to each other.
- the refrigerant paths 51, 52, and 53 are arranged in this order from the upstream side to the downstream side of the flow of the regeneration air.
- the refrigerant paths 51, 52, and 53 are arranged in this order from the downstream side to the upstream side of the flow of the regeneration air.
- FIG. 15 is an enlarged view showing the branch refrigerant paths 51 to 53 in the heat exchanger 300 e of the dehumidifier in FIG. 13.
- the branch refrigerant paths 51 to 53 penetrate the first heat exchange unit 310 and the second heat exchange unit 320. That is, as shown in FIG. 15, the branching refrigerant path 5 includes, in order from the condenser 220 side, the evaporating section 25 1 Aa, the condensing section 25 2 Aa, and the condensing section 25 2 A b, evaporating section 25 1 Ab, evaporating section 25 1 A c, and condensing section 25 2 A c.
- the branch refrigerant path 52 includes the evaporating section 25 1 B a, the condensing section 25 2 B a, the condensing section 25 2 B b, the evaporating section 25 1 B b, and the evaporating section 25 1 B c, condensing section 25 2 B c.
- the branch refrigerant path 53 includes an evaporating section 25 lC a, a condensing section 25 52 C a, a condensing section 25 2 C b, and an evaporating section. It has Yong 25 1 Cb, evaporating section 25 1 Cc and condensing section 25 2 Cc. In FIG.
- points a to d are the same as those in the third embodiment shown in FIG.
- the refrigerant liquid that has been cooled in the condenser 220 and has reached the state shown by the point d is divided into the branch refrigerant paths 51 to 53 and flows into the heat exchanger 300 e.
- the refrigerant passing through the refrigerant path 52 will be described.
- the refrigerant liquid that has flowed into the refrigerant passage 52 is decompressed by the throttle 332a, and flows into the evaporating section 251Ba of the first heat exchange unit 310.
- the state at this time is indicated by a point e, where a part of the liquid is evaporated and the liquid and the gas are mixed.
- the pressure at this time is an intermediate pressure between the condensing pressure of the condenser 220 and the evaporating pressure of the evaporator 2.10.
- 1.89 MPa and 0.30 MP It is a value between a.
- the refrigerant liquid evaporates under the above-mentioned intermediate pressure, and the state becomes a point 1 located at the same pressure between the saturated liquid line and the saturated gas line. In this state, part of the liquid has evaporated, but considerable refrigerant liquid remains. Then, the refrigerant in the state indicated by the point 1 flows into the condensation sections 2552Ba and 2552Bb.
- the condensing sections 25 2 B a and 25 2 B b the refrigerant is deprived of the heat by the low-temperature air in the state of the point P flowing through the second heat exchanging section 3 Reach.
- the refrigerant in the state of the point g1 flows into the evaporating sections 25 1 Bb and 25 1 Bc, where heat is deprived and the liquid phase is reduced to reach the state of the point f2. It enters the condensing section 25 2 Bc. In the condensing section 25 2 B c, the refrigerant increases its liquid phase and reaches the state at point g 2. The point g2 is located on the saturated liquid line in the Mollier diagram. At this time, the temperature of the refrigerant is 11 ° C, and the enthalpy is 21.5OkJ / kg.
- the refrigerant liquid in the state at the point g2 is reduced in pressure to 0.3 OMPa which is a saturation pressure at a temperature of 1 ° C by the throttle 3332b, and reaches a state shown by a point q.
- the refrigerant in the state at the point q reaches the evaporator 210 as a mixture of the refrigerant liquid and gas at 1 ° C, where it takes heat from the air at the point V, evaporates and evaporates to the state shown at the point a.
- This saturated gas is sucked into the regenerative booster 260, and the above-described cycle is repeated.
- the refrigerant passing through the refrigerant path 51 passes through the restriction 3311a, the evaporating section, the condensing section, and the restriction 3311b, and passes through the points j, i1, k1, i2, and k2.
- the state shown by point 1 is reached through the state shown by.
- the refrigerant passing through the refrigerant path 53 passes through the restriction 33 33 a, the evaporating section, the condensing section, and the restriction 33 33 b, and passes through the point m, the point n1, the point o1, the point n2 and the point. Indicated by 2
- the state reaches the state indicated by the point r through the state.
- the refrigerant changes its state of evaporation from point e to point f 1 or from point g 1 to point f 2 in the evaporator section,
- the condensed state changes from point f1 to point g1, or from point ⁇ 2 to point g2, and the heat transfer coefficient is extremely high because of the evaporation and condensation heat transfer. And heat exchange efficiency is high.
- a compression heat pump HP5 including a booster 260, a condenser 220, a throttle 3311a to 3333b, and an evaporator 210. 0 e and surrounding refrigerant and air paths are omitted in the drawing). If the heat exchanger 300 e according to the present invention is provided, the gas circulating to the booster for the same cooling load is considered. The amount and, consequently, the required power can be significantly reduced as in the third embodiment. That is, the same operation as the subcool cycle can be provided.
- the dehumidifier of the present invention reduces the refrigerant enthalpy at the inlet of the evaporator 210 due to the economizer effect of the heat pump HP5, and has a high refrigerant refrigerating effect per unit flow rate. Energy efficiency is increased.
- the present invention is not limited to the above-described embodiments, and may be embodied in various forms within the scope of the technical idea.
- the number of evaporating sections in the first heat exchanging section and the number of condensing sections in the second heat exchanging section of each refrigerant path are not limited to those shown.
- the number of branches of the branched refrigerant path in the fifth embodiment is not limited to the number shown in the drawing, and the refrigerant path may be branched into any number of rows.
- the desiccant rotor 103 is formed as a thick disk-shaped rotor that rotates around a rotation axis AX, and the rotor is filled with a desiccant with a gap through which gas can pass.
- a large number of tubular drying elements 103a are bundled so that the central axis thereof is parallel to the rotation axis AX.
- the rotor 103 rotates in one direction around the rotation axis AX, and the processing air A and the regeneration air B flow in and out of the rotation axis AX, respectively.
- Each drying element is arranged so as to alternately contact the processing air A and the regeneration air B as the desiccant rotor 103 rotates.
- the processing air A and the regeneration air B are each circularly parallel to the rotation axis AX. It is configured to flow in a substantially half area of the citrant rotor 103 in a counterflow manner.
- the region where the processing air A flows and the region where the regeneration air B flows are separated by a partition plate (not shown in FIG. 16), and the desiccant rotor 103a rotates across the partition plate,
- the drying element 103 a comes into contact with the processing air A and the regeneration air B alternately.
- the rotor is partially cut away.
- the desiccant may be filled in the tubular drying element described above.
- the desiccant port 103 is configured so that the processing air A and the regeneration air B flow in the thickness direction of the disk-shaped rotor.
- the evaporator 210 cools the regeneration air B below the dew point, and the heat exchangers 300, 300b, 300c, and 300c pre-cool the regeneration air B. 0 d, 3 0 e
- First section 3 10 0, condenser 22 0 for heating regeneration air B, heat exchanger 3 0 0, 3 0 b, 3 for preheating regeneration air B
- the refrigerant system was simplified to a single unit, and the evaporator 2 10 Since the pressure difference between the condensers 220 can be used, the circulation becomes active, and the boiling phenomenon accompanied by the phase change can be applied to the heat exchange of pre-cooling and pre-heating. it can.
- the dehumidifying device for dehumidifying the air-conditioned space has been described.
- the dehumidifying device is not necessarily limited to the air-conditioned space, and the dehumidifying device of the present invention can be applied to other spaces requiring dehumidification.
- a moisture adsorbing device that adsorbs moisture of process air and is regenerated with regeneration air
- a condenser that heats the regeneration air upstream of the moisture adsorption device
- An evaporator that cools to a temperature below the dew point downstream of the adsorption device
- a booster that pressurizes the refrigerant evaporated by the evaporator and sends it to the condenser, and regenerated air that flows between the moisture adsorption device and the evaporator
- a heat pump having a heat exchanger for exchanging heat with regeneration air flowing between the evaporator and the condenser, wherein the regeneration air is configured to be circulated.
- the regeneration air can be pre-cooled by the heat exchange means before cooling in the evaporator, and the pre-cooled cold heat can be recovered from the regeneration air once cooled in the evaporator, and the heat pump having a high operation coefficient Therefore, it is possible to provide a dehumidifying device having a high dehumidifying ability per energy consumption.
- the treated air is not cooled by an evaporator to remove water, but is treated by a moisture adsorption device. Therefore, air with a low dew point below freezing, that is, air with a low absolute humidity below 4 g / kg DA can be obtained.
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002531447A JP3406593B2 (ja) | 2001-05-16 | 2001-05-16 | 除湿装置 |
PCT/JP2001/004072 WO2002093081A1 (fr) | 2001-05-16 | 2001-05-16 | Deshumidificateur |
US10/275,988 US6644059B2 (en) | 2001-05-16 | 2001-05-16 | Dehumidifying apparatus |
EP01930180A EP1388714A4 (en) | 2001-05-16 | 2001-05-16 | DEHUMIDIFIER |
CNB018107494A CN1180205C (zh) | 2001-05-16 | 2001-05-16 | 除湿装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2001/004072 WO2002093081A1 (fr) | 2001-05-16 | 2001-05-16 | Deshumidificateur |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002093081A1 true WO2002093081A1 (fr) | 2002-11-21 |
Family
ID=11737322
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2001/004072 WO2002093081A1 (fr) | 2001-05-16 | 2001-05-16 | Deshumidificateur |
Country Status (5)
Country | Link |
---|---|
US (1) | US6644059B2 (ja) |
EP (1) | EP1388714A4 (ja) |
JP (1) | JP3406593B2 (ja) |
CN (1) | CN1180205C (ja) |
WO (1) | WO2002093081A1 (ja) |
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Also Published As
Publication number | Publication date |
---|---|
US6644059B2 (en) | 2003-11-11 |
JP3406593B2 (ja) | 2003-05-12 |
CN1180205C (zh) | 2004-12-15 |
US20030136140A1 (en) | 2003-07-24 |
CN1433511A (zh) | 2003-07-30 |
JPWO2002093081A1 (ja) | 2004-09-02 |
EP1388714A4 (en) | 2008-04-09 |
EP1388714A1 (en) | 2004-02-11 |
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