WO2015136653A1 - Appareil de déshumidification - Google Patents

Appareil de déshumidification Download PDF

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Publication number
WO2015136653A1
WO2015136653A1 PCT/JP2014/056568 JP2014056568W WO2015136653A1 WO 2015136653 A1 WO2015136653 A1 WO 2015136653A1 JP 2014056568 W JP2014056568 W JP 2014056568W WO 2015136653 A1 WO2015136653 A1 WO 2015136653A1
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Prior art keywords
operation mode
heat exchanger
air
dehumidifying
detection device
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PCT/JP2014/056568
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English (en)
Japanese (ja)
Inventor
畝崎　史武
伊藤　慎一
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三菱電機株式会社
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Priority to PCT/JP2014/056568 priority Critical patent/WO2015136653A1/fr
Publication of WO2015136653A1 publication Critical patent/WO2015136653A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/261—Drying gases or vapours by adsorption
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/02—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols by adsorption, e.g. preparative gas chromatography
    • B01D53/04—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols by adsorption, e.g. preparative gas chromatography with stationary adsorbents
    • B01D53/0407—Constructional details of adsorbing systems
    • B01D53/0438—Cooling or heating systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D2253/00—Adsorbents used in seperation treatment of gases and vapours
    • B01D2253/10—Inorganic adsorbents
    • B01D2253/106—Silica or silicates
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D2253/00—Adsorbents used in seperation treatment of gases and vapours
    • B01D2253/10—Inorganic adsorbents
    • B01D2253/106—Silica or silicates
    • B01D2253/108—Zeolites

Definitions

  • the present invention relates to a dehumidifying device.
  • Patent Document 1 As a dehumidifying device that dehumidifies the inside of a dehumidifying target space by using adsorption / desorption by a desiccant material that adsorbs and desorbs moisture.
  • Patent Document 1 is a technique for performing dehumidification by combining cooling and heating by a heat exchanger of a refrigeration cycle and adsorption / desorption by a desiccant rotor.
  • the air in the dehumidification target space is desorbed from the radiator of the refrigeration cycle and the desiccant rotor. Part, the evaporator of the refrigeration cycle, and the air passage through which the adsorbing part of the desiccant rotor passes.
  • the air in the air to be dehumidified taken into this air passage is heated by a radiator, the heated air is humidified by the desorption part of the desiccant rotor, and the humidified air is cooled to below the dew point temperature by an evaporator to cool and dehumidify.
  • the dehumidified air is further dehumidified by the adsorbing part of the desiccant rotor and then returned to the dehumidifying target space. And it is set as the structure which performs a dehumidification driving
  • the present invention has been made to solve the above-described problems, and eliminates the need for a desiccant rotor drive unit and a seal structure at the boundary between the adsorbing unit and the desorbing unit while having a high dehumidifying capacity. It is an object of the present invention to realize a dehumidifying apparatus that can simplify the apparatus and can be made compact and low in cost.
  • a dehumidifying device includes a refrigerant circuit in which a compressor, a flow path switching device, a first heat exchanger, a decompression device, and a second heat exchanger are sequentially connected by a refrigerant pipe, a first heat exchanger, An air passage in which a desiccant material capable of adsorbing and desorbing and a second heat exchanger are arranged in series; and a blower device that is provided in the air passage and allows air in the dehumidification target space to flow into the air passage.
  • the exchanger operates as a condenser or a radiator
  • the second heat exchanger operates as an evaporator
  • a first operation mode in which moisture held in the desiccant material is desorbed
  • the first heat exchanger is an evaporator
  • the second heat exchanger operates as a condenser or a radiator
  • the second operation mode in which the desiccant material adsorbs moisture from the air passing through the air path is alternated by switching the flow path of the flow path switching device.
  • the dehumidifying operation to switch to is performed.
  • the present invention it is possible to perform dehumidification with a high dehumidification amount by combining the adsorption / desorption action of the desiccant material with the cooling and heating action by the refrigeration cycle operation of the refrigerant circuit.
  • the first heat exchanger, the desiccant material, and the second heat exchanger are arranged in series, and the first heat exchanger operates as a condenser or a radiator, and the second heat exchange.
  • the dehumidifying operation is performed by alternately switching the second operation mode in which the desiccant material absorbs moisture from the air passing through the air passage by switching the flow path of the flow path switching device, the device structure is simplified. Therefore, a more compact and low-cost device can be obtained.
  • FIG. 1 is a diagram showing a configuration of a dehumidifying device according to Embodiment 1 of the present invention.
  • the dehumidifying device 1 includes a compressor 2, a four-way valve 3 that is a flow path switching device, a first heat exchanger 4, an expansion valve 5 that is a decompression device, and a second heat exchanger 6 in a housing 10. These are connected in an annular shape by a refrigerant pipe to constitute a refrigerant circuit A.
  • the inside of the housing 10 is divided into an air passage chamber 20 and a machine chamber 30.
  • the compressor 2 and the four-way valve 3 are arranged in the machine chamber 30, and the others are arranged in the air passage chamber 20.
  • a through hole (not shown) is formed in the wall surface 11 partitioning the machine room 30 and the air passage chamber 20, and a refrigerant pipe is passed through the through hole (not shown) to connect each element. Is connected.
  • the four-way valve 3 can switch the flow path so that the refrigerant flows in the solid line direction or the dotted line direction in FIG. 1, and when switched to the solid line flow path in FIG. 1, the refrigerant discharged from the compressor 2 flows.
  • the four-way valve 3, the first heat exchanger 4, the expansion valve 5, the second heat exchanger 6, and the four-way valve 3 flow in that order to return to the compressor 2.
  • the first heat exchanger 4 operates as a condenser (heat radiator), and the second heat exchanger 6 operates as an evaporator.
  • the refrigerant discharged from the compressor 2 is transferred to the compressor 2, the four-way valve 3, the second heat exchanger 6, and the expansion valve 5.
  • the refrigeration cycle that flows in the order of the first heat exchanger 4 and the four-way valve 3 and returns to the compressor 2 is configured.
  • the second heat exchanger 6 operates as a condenser (heat radiator), and the first heat exchanger 4 operates as an evaporator.
  • R410A is used as the refrigerant of the dehumidifier 1.
  • the refrigerant is not limited to R410A, and can be applied to other natural refrigerants such as HFC refrigerant, HC refrigerant, CO 2 , and NH 3 .
  • HFC refrigerant HFC refrigerant
  • HC refrigerant HC refrigerant
  • CO 2 CO 2
  • NH 3 NH 3
  • the first heat exchanger 4 and the second heat exchanger 6 are plate fin tube heat exchangers, and are configured to exchange heat between the refrigerant flowing in the heat transfer tubes and the air flowing around the fins.
  • the expansion valve 5 is a valve whose opening degree is fixed, and decompresses and expands the refrigerant passing therethrough.
  • the air channel chamber 20 has a suction port 20a for introducing air to be dehumidified therein, and an air outlet 20b for discharging the dehumidified air to the outside. In the direction of the white arrow in FIG. Air conveyed by the blower 8 flows.
  • the air passage chamber 20 is configured in a rectangular shape, and the first heat exchanger 4, the desiccant block 7 that is a desiccant material, the second heat exchanger 6, and the blower 8 are arranged in series in the air passage chamber 20. An air path B is formed.
  • the air sucked into the air passage B from the suction port 20a is straight in the air passage B in the order of the first heat exchanger 4, the desiccant block 7, which is a desiccant material, the second heat exchanger 6, and the blower 8. After flowing in the shape, the air is exhausted to the outside of the dehumidifier 1 from the air outlet 20b.
  • the desiccant block 7 is formed by molding a desiccant material into a solid and rectangular shape.
  • the desiccant block 7 is made of a material that absorbs and desorbs moisture. For example, zeolite, silica gel, a polymer adsorbent, and the like are applied.
  • a drain pan 40 is disposed below each of the first heat exchanger 4 and the second heat exchanger 6, and drain water generated during operation is dripped from each heat exchanger. ing.
  • the drain water received by the drain pan 40 flows into the drain tank 42 at the lowermost part of the dehumidifier 1 via the water channel 41 shown by the broken line in FIG.
  • the air passage chamber 20 further includes a temperature / humidity sensor 50 that measures the temperature / humidity of the intake air of the dehumidifier 1 (temperature / humidity around the dehumidifier 1).
  • a control device 60 for controlling the entire dehumidifying device 1 is provided on the machine room 30 side.
  • the control device 60 is constituted by a microcomputer and includes a CPU, a RAM, a ROM, and the like, and a control program is stored in the ROM.
  • the control device 60 controls the dehumidifying operation described later (switching of the four-way valve 3 according to the detection signal of the temperature / humidity sensor 50), the rotational speed control of the blower 8, the rotational speed control of the compressor 2, and the opening of the expansion valve 5.
  • Various controls such as degree control are performed.
  • the dehumidifying operation operation of the dehumidifying device 1 will be described.
  • the dehumidifying device 1 two operation modes are realized by switching the flow path of the four-way valve 3.
  • it demonstrates in order.
  • First operation mode operation of the refrigeration cycle
  • the operation of the refrigeration cycle in the first operation mode is as follows. After the low-pressure gas is sucked in by the compressor 2, it is compressed to become a high-temperature and high-pressure gas.
  • the refrigerant discharged from the compressor 2 flows into the first heat exchanger 4 through the four-way valve 3.
  • the refrigerant flowing into the first heat exchanger 4 dissipates heat to the air flowing through the air passage B, and while the air is heated, the refrigerant itself is cooled and condensed to become a high-pressure liquid refrigerant from the first heat exchanger 4.
  • the liquid refrigerant flowing out from the first heat exchanger 4 is decompressed by the expansion valve 5 and becomes a low-pressure two-phase refrigerant. Thereafter, the refrigerant flows into the second heat exchanger 6, absorbs heat from the air flowing through the air passage B, and while the air is cooled, the refrigerant itself is heated and evaporated to become low-pressure gas. Thereafter, the refrigerant is sucked into the compressor 2 through the four-way valve 3.
  • FIG. 2 is an air wetting diagram showing air state changes in the first operation mode, where the vertical axis represents the absolute humidity of the air and the horizontal axis represents the dry bulb temperature of the air. Moreover, the curve of FIG. 2 shows saturated air, and the relative humidity in saturated air is 100%.
  • the air around the dehumidifier 1 flows into the dehumidifier 1 and is heated by the first heat exchanger 4 to increase the temperature and decrease the relative humidity (point B in FIG. 2). ). Thereafter, air flows into the desiccant block 7, but since the relative humidity of the air is low, the moisture held in the desiccant block 7 is desorbed (released), and the amount of moisture contained in the air increases. On the other hand, desorption heat accompanying desorption is deprived from the air flowing into the desiccant block 7, the temperature of the air is lowered, and the temperature becomes low and high humidity (point C in FIG. 2). Thereafter, the air flows into the second heat exchanger 6 and is cooled.
  • the refrigerant circuit A is operated such that the refrigerant temperature in the second heat exchanger 6 is lower than the dew point temperature of the air, and the air is cooled and dehumidified by the second heat exchanger 6, and the low temperature Thus, the absolute humidity is low (D point in FIG. 2). Thereafter, the air flows into the blower 8 and is exhausted from the air outlet 20b to the outside of the dehumidifier 1.
  • the operation of the refrigeration cycle in the second operation mode is as follows. After the low-pressure gas is sucked in by the compressor 2, it is compressed to become a high-temperature and high-pressure gas. The refrigerant discharged from the compressor 2 flows into the second heat exchanger 6 through the four-way valve 3. The refrigerant flowing into the second heat exchanger 6 radiates heat to the air flowing through the air passage B, and while the air is heated, the refrigerant itself is cooled and condensed to become a high-pressure liquid refrigerant. Spill from.
  • the liquid refrigerant flowing out of the second heat exchanger 6 is decompressed by the expansion valve 5 and becomes a low-pressure two-phase refrigerant. Thereafter, the refrigerant flows into the first heat exchanger 4, absorbs heat from the air flowing through the air passage B, and while the air is cooled, the refrigerant itself is heated and evaporated to become a low-pressure gas. Thereafter, the refrigerant is sucked into the compressor 2 through the four-way valve 3.
  • FIG. 3 is an air wetting diagram showing the air state change in the second operation mode, where the vertical axis represents the absolute humidity of the air and the horizontal axis represents the dry bulb temperature of the air. Moreover, the curve of FIG. 3 shows saturated air, and the relative humidity in saturated air is 100%.
  • the air around the dehumidifying device 1 flows into the dehumidifying device 1 and is then cooled by the first heat exchanger 4.
  • the refrigerant circuit A is operated such that the refrigerant temperature in the first heat exchanger 4 is lower than the dew point temperature of the air, and the air is cooled and dehumidified by the first heat exchanger 4 so that the temperature is low.
  • a high relative humidity state (FIG. 3, point E).
  • the air flowing into the desiccant block 7 is heated by the heat of adsorption generated along with the adsorption, and the temperature of the air rises to a high temperature and low humidity state (point F in FIG. 3). Then, air flows into the 2nd heat exchanger 6, is heated, and becomes high temperature (FIG. 3, G point). Thereafter, the air flows into the blower 8 and is exhausted from the air outlet 20b to the outside of the dehumidifier 1.
  • the second operation mode dehumidification by adsorption of the desiccant block 7 is performed in addition to dehumidification by cooling with the refrigerant in the first heat exchanger 4. Therefore, as apparent from a comparison between FIG. 2 and FIG. 3, the second operation mode can secure a larger amount of dehumidification than the first operation mode, and the main dehumidification with the present dehumidifier 1 is the second dehumidification amount. It will be carried out in the operation mode.
  • the first and second operation modes are alternately repeated.
  • the amount of moisture contained in the desiccant block 7 has an upper limit. Therefore, if the operation is performed for a certain time or longer, moisture is not adsorbed on the desiccant block 7 and the dehumidification amount decreases. . Therefore, when the amount of moisture retained in the desiccant block 7 is close to the upper limit, the operation mode is switched to the first operation mode and the operation of releasing moisture from the desiccant block 7 is performed. The first operation mode is carried out for a while, and the operation mode is switched again to the second operation mode when the amount of moisture retained in the desiccant block 7 is appropriately reduced.
  • the adsorption / desorption action of the desiccant block 7 is sequentially performed, and the effect of increasing the dehumidification amount due to the adsorption / desorption action of the desiccant is maintained.
  • the air passage B is configured linearly in configuring the high-performance dehumidifier 1 that combines the desiccant material adsorption / desorption action and the heating / cooling action of the refrigeration cycle. ing. Since the conventional device uses a desiccant rotor, it is necessary to ventilate the adsorbing part and the desorbing part of the desiccant rotor. The pressure loss when doing so was large. On the other hand, in this Embodiment 1, since the air path B was comprised linearly, the pressure loss at the time of conveying air can be made small. Therefore, the power consumption of the blower 8 that conveys air can be reduced correspondingly, and a more efficient device can be obtained.
  • the air passage B is formed in a rectangular shape. For this reason, when each of the 1st heat exchanger 4, the 2nd heat exchanger 6, and the desiccant block 7 mounted in the air path B is made into the rectangular external structure according to the shape of the air path B, a rectangular air path B can be mounted at a higher density.
  • a conventional apparatus uses a desiccant rotor, a circular rotor is disposed in a rectangular air passage B. Therefore, dead spaces are formed at the four corners in the rotor arrangement portion, and the air passage cannot be made compact.
  • the rectangular desiccant block 7 by using the rectangular desiccant block 7, it can be arranged without dead space, so that high-density mounting is possible. As a result, the air passage B can be made compact (the air passage chamber 20 is compact).
  • the conventional apparatus it is necessary to separate the air path between the adsorption part and the desorption part, and a seal structure that hermetically separates the boundary part between the adsorption part and the desorption part is necessary.
  • a seal structure that hermetically separates the boundary part between the adsorption part and the desorption part is necessary.
  • the first embodiment there is only one air passage B, and by switching the four-way valve 3, the adsorption and desorption of the desiccant block 7 can be switched, so a conventional seal structure is unnecessary.
  • the apparatus configuration can be simplified and the cost can be reduced.
  • each of the 1st heat exchanger 4, the 2nd heat exchanger 6, and the desiccant block 7 mounted in the air path B is made into the structure where the external shape is a rectangle according to the shape of the air path B as mentioned above. As described above, it is preferable because the effect of downsizing can be obtained, but it is not necessarily limited to a rectangle.
  • the air to be conveyed is heated by the second heat exchanger 6 after dehumidification by the first heat exchanger 4 and dehumidification by the desiccant block 7. Therefore, the blown air of the dehumidifier 1 is in a state where the amount of moisture is low at a high temperature (FIG. 3, point G), and the relative humidity can be set to a low relative humidity of, for example, 20% or less.
  • Such low relative humidity air is air suitable for drying applications, and if this air is directly applied to an object to be dried such as laundry, drying of the object to be dried can be promoted. A higher performance drying function can be realized.
  • the blown air in the first operation mode is lower in temperature and humidity than the blown air in the second operation mode. Therefore, when the dehumidifier 1 is used for drying an object to be dried, the second operation mode is used. It is desirable to apply blown air to the object to be dried only when Therefore, in order to cope with such a use, the vane 20b of the dehumidifier 1 is provided with a vane capable of changing the blowing air direction, and the blowing direction in the first operation mode and the blowing direction in the second operation mode are separated. It is good also as a structure which can be adjusted to the direction. And only in the second operation mode, the vane may be adjusted so that the air blown from the air outlet 20b hits the object to be dried. Thereby, drying of the object to be dried can be further promoted, and a high-performance drying function can be achieved. realizable.
  • the dehumidifying device of the present invention is not limited to the above-described configuration, and can be variously modified as follows without departing from the gist of the present invention.
  • FIG. 1 shows a configuration using the four-way valve 3 for switching the refrigerant circuit A
  • the configuration is not particularly limited to the four-way valve as long as the flow path of the refrigerant circuit A can be switched. May be used.
  • four solenoid valves which are two-way valves, are used to connect the discharge side and the suction side of the compressor 2 to the first heat exchanger 4, and the discharge side and the suction side of the compressor 2. It is good also as a structure which has arrange
  • Each operation time in the first operation mode and the second operation mode may be a predetermined time, but each operation time in each operation mode is appropriate according to the air condition or the operation state of the dehumidifier 1. There is a value. Therefore, the operation time of each operation mode may be determined based on the air condition or the operation state of the dehumidifier 1 so that the operation can be performed with the appropriate value.
  • the first operation mode moisture is released from the desiccant block 7, so that an appropriate amount of moisture is released from the desiccant block 7 and the time required for the amount of water remaining in the desiccant block 7 to be an appropriate amount is an appropriate value. It becomes.
  • the second operation mode is switched to the desiccant block 7 with a larger amount of water remaining than the appropriate amount, the amount of water that can be adsorbed by the desiccant block 7 in the second operation mode is suppressed. The amount of dehumidification in the second operation mode is reduced.
  • the first operation mode is made too long, the state in which moisture can hardly be desorbed from the desiccant block 7 will continue in the latter half of the first operation mode, and the second dehumidifying amount is higher than that in the first operation mode. Switching to operation mode is slow. Therefore, also in this case, the total amount of dehumidification is reduced.
  • the second operation mode moisture is adsorbed on the desiccant block 7, so that the time when the adsorbed moisture amount on the desiccant block 7 becomes an appropriate amount is an appropriate value. Even though there is still room for adsorption by the desiccant block 7, when the operation is switched to the first operation mode, the operation time of the second operation mode with a high dehumidification amount is shorter than the first operation mode, The amount of dehumidification is reduced when viewed. On the other hand, if the second operation mode is set too long, the desiccant block 7 cannot continue to be adsorbed in the second half of the second operation mode, and the dehumidification amount is reduced in this case as well.
  • the change in the amount of moisture retained in the desiccant block 7 is determined by the relative humidity of the air flowing into the desiccant block 7.
  • the moisture in the desiccant block 7 is difficult to be released, and conversely, the moisture adsorption amount is Become more.
  • air having a low relative humidity flows into the desiccant block 7 the moisture in the desiccant block 7 is easily released, and the moisture adsorption amount is reduced.
  • the operation time of each operation mode may be determined by the following method 1 or method 2.
  • the first operation mode and the second operation mode are set as one cycle, and this cycle is repeated.
  • the time of one cycle that is, the operation time of the first operation mode and the operation time of the second operation mode
  • the total time is always the same. Therefore, in the determination method described below, the time distribution of each of the first operation mode and the second operation mode within one cycle is determined.
  • Each operation time is determined at the start of the dehumidifying operation.
  • each determination pattern will be described in order.
  • the relative humidity of the intake air is obtained from the state of the intake air obtained by the temperature / humidity sensor 50, and the operation time of each operation mode is determined according to the relative humidity. This will be specifically described below.
  • Standard operation for each operation mode that can determine the relative humidity (hereinafter referred to as “reference relative humidity”) as a reference for the intake air, and can achieve a high dehumidification amount when the intake air of the reference relative humidity passes through the air passage B.
  • the time is obtained in advance by experiment or simulation. Then, depending on the magnitude relationship between the actual relative humidity of the intake air and the reference relative humidity, the operation time for each operation mode is determined by appropriately increasing or decreasing the reference operation time for each operation mode as described below. To do.
  • the desiccant block in the first operation mode is less than the amount of moisture released when the relative humidity is the reference relative humidity, and the amount of moisture adsorbed by the desiccant block 7 in the second operation mode is the same as when the relative humidity is the reference relative humidity. More than the amount of moisture adsorption.
  • the operation time in the first operation mode is made longer than the reference operation time corresponding to the first operation mode, and conversely, the operation time in the second operation mode is set to be longer. Shorter than the reference operation time corresponding to the second operation mode.
  • the amount of moisture released from the desiccant block 7 in the first operation mode is greater than the amount of moisture released when the relative humidity is the reference relative humidity.
  • the moisture adsorption amount of the desiccant block 7 in the second operation mode is smaller than the moisture adsorption amount when the relative humidity is the reference relative humidity. Therefore, when the actual relative humidity of the intake air is lower than the reference relative humidity, the operation time in the first operation mode is made shorter than the reference operation time corresponding to the first operation mode, and conversely, the operation time in the second operation mode is reduced. It is longer than the reference operation time corresponding to the second operation mode.
  • Determination method 2 Each operation time of each operation mode is determined according to the operation state of the refrigerant circuit A at the start of the dehumidifying operation. This will be specifically described below.
  • the operating state of the refrigerant circuit A varies depending on the state of the intake air. Specifically, when the relative humidity of the intake air is high, the humidity difference between the air before and after passing through the heat exchanger that serves as an evaporator in each operation mode is larger than when the relative humidity of the intake air is low. . That is, since heat exchange between the refrigerant and air in the evaporator is promoted, an operation in which the low-pressure pressure of the refrigeration cycle is increased accordingly. On the contrary, when the relative humidity of the intake air is low, heat exchange between the refrigerant and the air in the evaporator is suppressed, so that the low pressure of the refrigeration cycle is reduced.
  • the first and second values are determined according to the low pressure of the refrigeration cycle.
  • the operation time of each operation mode can be determined.
  • the operation time for each of the first operation mode and the second operation mode is determined according to the low pressure or the high pressure of the refrigeration cycle. it can.
  • the low pressure (or high pressure) of the refrigeration cycle is measured, and the measured low pressure value (or measured high pressure value) obtained by measurement and the predetermined low pressure reference value (or high pressure reference value).
  • the measured low pressure value (or measured high pressure value) is higher than the low pressure reference value (or high pressure reference value)
  • the operation time in the operation mode is made longer than the reference operation time, and conversely, the operation time in the second operation mode is made shorter than the reference operation time.
  • the operation time is made shorter than the reference operation time, and conversely, the operation time in the second operation mode is made longer than the reference operation time.
  • the low pressure and high pressure may be measured by providing pressure sensors in the low pressure part and high pressure part of the refrigeration cycle, or the refrigerant temperature of each heat exchanger that becomes a gas-liquid two-phase part in the refrigeration cycle. May be measured and a low pressure may be estimated from the temperature.
  • the second operation mode when it is estimated that frost formation has occurred in the first heat exchanger 4 due to the operation state of the refrigerant circuit A, before the end of the preset operation time (or the determination method described above) 1 and before the end of the operation time determined by the determination method 2), the second operation mode may be ended and switched to the first operation mode.
  • the first operation mode since the first heat exchanger 4 operates as a condenser, the refrigerant is at high pressure and high temperature, so that frost can be heated and melted.
  • the frost formation state can be determined by the low pressure of the refrigeration cycle. For example, when the low pressure is lower than a predetermined value during the operation in the second operation mode, the fins of the first heat exchanger 4 are It is determined that the state where the surface temperature is 0 ° C. or lower continues for a long time and frost formation has progressed. In this case, as described above, the second operation mode is terminated and switched to the first operation mode.
  • the low pressure measurement method is similar to the above-described means, in which a pressure sensor is provided in the low pressure part of the refrigeration cycle, or the refrigerant temperature of the first heat exchanger 4 that becomes a gas-liquid two-phase part at low pressure may be measured. .
  • the dehumidifying device 1 when the frosting state is determined in the second operation mode, switching to the first operation mode eliminates the operation while the frosting state proceeds, and the dehumidification amount decreases due to the decrease in the air flow rate. Thus, the dehumidifying device 1 with higher reliability can be realized.
  • FIG. FIG. 4 is a diagram showing the configuration of the dehumidifying device according to Embodiment 2 of the present invention.
  • the second embodiment will be described focusing on the differences from the first embodiment. Note that the modification applied to the same components as those in the first embodiment is similarly applied to the second embodiment.
  • the dehumidifying device 100 of the second embodiment the four-way valve 3 is removed from the dehumidifying device 1 of the first embodiment shown in FIG. 1, and the flow direction of the refrigerant in the refrigerant circuit A is limited to the solid arrow direction in FIG. It has the structure made.
  • a blower 8 b is provided between the suction port 20 a and the first heat exchanger 4.
  • the suction port 20a serves as a suction blower outlet 20a that performs not only suction but also blows out
  • the blower outlet 20b serves as a suction blower outlet 20b that performs suction as well as blowout.
  • the dehumidifier 100 further includes a temperature / humidity sensor 50b that measures the temperature and humidity of the air flowing from the suction outlet 20b (temperature and humidity around the dehumidifier 100).
  • a temperature / humidity sensor 50b that measures the temperature and humidity of the air flowing from the suction outlet 20b (temperature and humidity around the dehumidifier 100).
  • One of the configurations may be adopted. In short, it is only necessary to detect the temperature and humidity of the intake air of the dehumidifier 100.
  • the blower 8 and the blower 8b are not operated at the same time, but are operated one by one.
  • air flows in the direction of the white arrow from the left to the right in FIG. 4 (first direction) as in FIG. 1, and when the blower 8b is operated, from the right of FIG. Air flows in the direction of the gray arrow to the left (second direction).
  • the two air blowers were shown here as an air blower which flows air in the direction of a white arrow or the direction of a gray arrow, it can rotate forward and reverse and can be blown in both directions of the white arrow and the gray arrow It is good also as an air blower.
  • the first heat exchanger 4 always operates as a condenser and heats inflowing air.
  • the second heat exchanger 6 always operates as an evaporator, and cools and dehumidifies the incoming air.
  • the second embodiment has a third operation mode in which the blower 8 is operated to flow air in the direction of the white arrow, and a fourth operation mode in which the blower 8b is driven to flow air in the direction of the gray arrow, Switch the operation mode to dehumidify.
  • the third operation mode is the same operation as the first operation mode in the first embodiment, and the air flowing into the air passage B from the suction outlet 20a is heated by the first heat exchanger 4 and has a low relative humidity. After that, the moisture retained in the desiccant block 7 is desorbed, and then flows into the second heat exchanger 6 to be cooled and dehumidified, and then blown out of the dehumidifier 100 from the suction outlet 20b.
  • the fourth operation mode after the air flowing into the air passage B from the suction outlet 20b is cooled and dehumidified by the second heat exchanger 6 to become a high relative humidity, moisture is adsorbed to the desiccant block 7. Further, dehumidification is performed, and thereafter, heating is performed by the first heat exchanger 4 so as to be blown out of the dehumidifier 100 from the suction outlet 20a.
  • the refrigeration cycle operation of the refrigerant circuit A is different from that in the first embodiment, but the state change of the air in the air passage B is the same as in the second operation mode in the first embodiment.
  • the third and fourth operation modes are alternately repeated.
  • the state change of the air in the desiccant block 7 and the dehumidifier 100 is the same as that in the first embodiment when the first and second operation modes are alternately performed.
  • each operation time of the 3rd and 4th operation mode is the same as that of Embodiment 1. That is, the operation time of the third operation mode is determined in the same manner as the operation time of the first operation mode of the first embodiment, and the operation time of the fourth operation mode is the operation time of the second operation mode of the first embodiment. Determine in the same way. In addition, what is necessary is just to obtain
  • the same effect as in the first embodiment can be obtained. That is, in addition to being able to configure a high-performance dehumidifying device 100 that combines the desiccant material adsorption / desorption action and the cooling action of the refrigeration cycle, the air path configuration can be mounted with high density and simplified, and the equipment can be made compact and low Can be manufactured at low cost.
  • the relative humidity of the intake air is determined from the state of the intake air obtained by the temperature / humidity sensor 50 and the temperature / humidity sensor 50b.
  • Sensing means may be used.
  • means such as estimating the relative humidity from a sensor that directly measures the relative humidity or a sensor that measures the dew point temperature may be used.
  • the temperature / humidity sensor 50 and the temperature / humidity sensor 50b function as the state detection device of the present invention.
  • the detection sensor used for the measurement of the low pressure and the high pressure corresponds to the state detection device of the present invention as described above.
  • 1 Dehumidifier 1 Compressor, 3 Four-way Valve, 4 1st Heat Exchanger, 5 Expansion Valve, 6 2nd Heat Exchanger, 7 Desiccant Block, 8 Blower, 8b Blower, 10 Housing, 11 Wall, 20 Airway Room, 20a inlet (suction outlet), 20b outlet (suction outlet), 30 machine room, 40 drain pan, 41 water channel, 42 drain tank, 50 temperature / humidity sensor, 50b temperature / humidity sensor, 60 control device, 100 dehumidification Equipment, A refrigerant circuit, B air path.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Drying Of Gases (AREA)

Abstract

Sont montés en série un premier échangeur de chaleur (4), un bloc déshydratant (7), et un deuxième échangeur de chaleur (6). Des opérations de déshumidification sont répétées successivement : un premier mode opérationnel dans lequel le premier échangeur de chaleur (4) fonctionne comme condenseur ou radiateur et le deuxième échangeur de chaleur (6) fonctionne comme évaporateur, et un deuxième mode opérationnel dans lequel le premier échangeur de chaleur (4) fonctionne comme évaporateur et le deuxième échangeur de chaleur (6) fonctionne comme condenseur ou radiateur.
PCT/JP2014/056568 2014-03-12 2014-03-12 Appareil de déshumidification WO2015136653A1 (fr)

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PCT/JP2014/056568 WO2015136653A1 (fr) 2014-03-12 2014-03-12 Appareil de déshumidification

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PCT/JP2014/056568 WO2015136653A1 (fr) 2014-03-12 2014-03-12 Appareil de déshumidification

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013061829A1 (fr) * 2011-10-27 2013-05-02 三菱電機株式会社 Déshumidificateur

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013061829A1 (fr) * 2011-10-27 2013-05-02 三菱電機株式会社 Déshumidificateur

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