JP4541965B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner, and more particularly to an air conditioner having a dehumidifying function.

A conventional air conditioner having a dehumidifying function includes a compressor, a condenser, an expansion valve, an evaporator, and a defrost heater. The refrigerant is filled in the refrigeration cycle of the air conditioner. The refrigerant compressed by the compressor becomes a high-temperature and high-pressure gas refrigerant and is sent to the condenser. The refrigerant that has flowed into the condenser is liquefied by releasing heat into the air.
The liquefied refrigerant is decompressed by the expansion valve to become a gas-liquid two-phase flow state, gasified by absorbing heat from ambient air in the evaporator, and flows to the compressor. In particular, in a refrigerated / refrigerated warehouse, since the temperature must be controlled to be lower than 10 ° C, the evaporation temperature becomes lower than 0 ° C. For this reason, frost was generated in the evaporator and the cooling capacity was reduced.

Therefore, a defrost heater is attached to the evaporator and a defrosting operation is periodically performed. As a result, extra energy is consumed, causing a reduction in the efficiency of the air conditioner. Furthermore, after the defrosting operation, the temperature in the freezer / refrigerated warehouse increased, the load of the air conditioner increased, and the power consumption increased.
In addition, in the case of an air conditioner (room air conditioner, etc.) that can control the rotation speed of the compressor, the cooling load is reduced in the intermediate period of the cooling (rainy season, autumn, etc.), so by reducing the rotation speed of the compressor Was following the load. As a result, the evaporation temperature rose and the sensible heat of the room could be removed, but the latent heat could not be removed, the relative humidity of the room increased, and the discomfort increased.

  Accordingly, an invention is disclosed in which a refrigerant refrigerator and a moisture adsorption unit are combined, and moisture in the air flowing into the evaporator (heat absorber) is removed in advance by the moisture adsorption unit, thereby eliminating the defrosting operation. That is, the air dehumidified by the desiccant rotor which is a moisture adsorption means is supplied to the evaporator (heat absorber). On the other hand, high temperature air heated by a condenser (heat radiator) is supplied to the moisture adsorbing means in order to desorb and regenerate the moisture adsorbed by the moisture adsorbing means (see, for example, Patent Document 1).

  FIG. 1 is a moisture equilibrium adsorption characteristic diagram showing the moisture equilibrium adsorption characteristic of zeolite. In a conventional air conditioner having a dehumidifying function, zeolite or silica gel is used as a solid adsorbent provided on the surface of a desiccant rotor. In the case of using zeolite as the solid adsorbent, it can be seen that in order to efficiently desorb and regenerate the moisture adsorbed on the zeolite, it is necessary to supply air having a relative humidity of several percent or less (see FIG. 1).

That is, in order to reduce the relative humidity of the air, it is necessary to heat the air to a high temperature. Therefore, CO ₂ (carbon dioxide) is used as the refrigerant, assuming that the heat dissipated by the condenser becomes relatively high. A refrigeration cycle is used in which the compressor compresses above the critical pressure of CO ₂ . The high pressure compressed by the compressor is about 100 to 150 [kgf / cm ² ], which is about twice that of a refrigeration cycle that does not exceed the normal critical pressure using HFC (hydrofluorocarbon) as a refrigerant. In order to ensure the pressure resistance of the compressor, the condenser, and the piping connecting them, the product cost will increase.

  Further, since the regeneration temperature of the solid adsorbent is as high as about 150 ° C., it is necessary to increase the air temperature at the outlet of the condenser. For this purpose, it is necessary to reduce the air volume at the condenser, and as a result, the high pressure is reduced. There is a problem that the compression ratio of the compressor increases and the efficiency of the compressor decreases (see, for example, Non-Patent Document 1).

  In addition, when silica gel is used as the solid adsorbent, it is known that silica gel has two types of adsorption characteristics. That is, the same problem as when using the above silica gel is applied to those having the same characteristics as zeolite, in which the water absorption rate is increased in the region where the relative humidity is low and the absorption rate is saturated in the region where the relative humidity is high. There is. In addition, the relative relative humidity differs in the relative relative humidity in the range where the water absorption rate is low for those having a characteristic that the absorption rate is low in the region where the relative relative humidity is low and the absorption rate is high in the region where the relative relative humidity is high. There is a problem that there is a restriction in dehumidifying the air-conditioned space by repeating adsorption and desorption (see Non-Patent Document 2).

Japanese Patent Laid-Open No. 2001-241893 (pages 6 to 8, FIG. 2) Yoshinori Enomoto, Jiro Okajima, Fumio Matsuoka, Satoshi Akizawa, Takao Kashiwagi, “Dehumidification / Humidification Rotor and System Performance Analysis 1st Report: Theoretical Model” Proceedings of Japan Society of Refrigeration and Air Conditioning Trans. Of the JSRAE Vol.19, No.3 (2002) pp.281-292 (page 287, equation (17)) “About Silica Gel”, Shin-Etsu Chemical Co., Ltd. website, [Search June 1, 2004], Internet <URL: http://www.shin-etsu-kasei.co.jp/silica.html>

  The present invention has been made to solve the above-described problems, and has a dehumidifying function by means of moisture adsorption, eliminates the need for heater heating, reduces the auxiliary heating amount of the heater, and reduces the efficiency of the compressor. An object of the present invention is to obtain an air conditioner that enables regeneration of the moisture adsorbing means by using the condensed exhaust heat in the refrigeration cycle.

In the air conditioner according to the present invention, the rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity is A moisture adsorbing means that is larger than the rate of change of the equilibrium adsorption amount with respect to the relative humidity outside the range of the relative humidity, and the first relative humidity and the second relative humidity are in the range of 30% to 40%;
Second air blowing means for supplying second air to which moisture is adsorbed by the moisture adsorption means;
First blowing means for supplying first air for desorbing moisture adsorbed on the moisture adsorbing means;
Driving means for driving the moisture adsorbing means to change a region to which the first air and the second air are supplied;
A refrigerant circuit that includes a compressor that is filled with refrigerant and compresses the refrigerant, a condenser that exchanges heat with the first air, a throttling device that expands the refrigerant, and an evaporator that exchanges heat with the second air;
Control means for controlling the supply amount of at least one or both of the first air and the second air ,
A first relative humidity sensor that detects the relative humidity of the first air that is disposed between the condenser and the moisture adsorption means, the condenser being disposed on the windward side of the first air with respect to the moisture adsorption means. When,
The second relative humidity is configured such that the evaporator is arranged on the leeward side of the second air with respect to the moisture adsorbing means, and detects the relative humidity of the second air installed between the evaporator and the moisture adsorbing means. A sensor, and
The control unit controls each of the first blowing unit and the second blowing unit based on detection results of the first relative humidity sensor and the second relative humidity sensor .

Since the air conditioning apparatus according to the present invention has the above-described configuration, the following significant effects are achieved.
(I) Conventionally, frequent defrosting operations can be eliminated, and power consumption can be reduced.
(Ii) Further, since it has a control means for controlling the supply amount of at least one of or both of the first air and the second air, the first air is set to a relative humidity suitable for desorption, and the second air is set to a relative suitable for adsorption. Since the humidity can be adjusted, highly efficient air conditioning is possible.
(Iii) Further, since the equilibrium adsorption rate fluctuates abruptly when the relative humidity of the moisture adsorbing means is 30% to 40%, about 30% relative to desorb and regenerate the moisture adsorbed on the moisture adsorbing means. Humid air is sufficient, and heating by the heater is not necessary just by heating the first air using the heat radiation of the condenser. Moreover, even if the amount of heating in the condenser is insufficient and auxiliary heating with the heater is required, the power consumption for heating the heater can be reduced.
(Iv) Furthermore, since a high regeneration temperature is not required, a high pressure that causes the refrigerant to exceed the critical pressure is not required in the compressor in the refrigerant circuit. Therefore, the pressure resistance of the compressor, the condenser and the piping connecting them can be lowered, the product cost can be reduced, and the compression ratio of the compressor can be suppressed, so the efficiency of the compressor can be improved, Energy saving is promoted.

[Embodiment 1]
(Air conditioner)
2 to 4 illustrate the air conditioner according to Embodiment 1 of the present invention. FIG. 2 is a schematic diagram, FIG. 3 is a schematic diagram of a desiccant rotor, and FIG. 4 is a schematic diagram of the air conditioner. It is the schematic explaining the drive state of the moisture adsorption means which is a part structure.
In this embodiment, an example in which the air conditioner is applied to a refrigerated warehouse is shown. FIG. 4 shows that the refrigerated room side 100a of the refrigerated warehouse has a dry air temperature of Tai [° C.] in the air state of the space and the second air. The inlet side relative humidity φa1 [%]. For the outside air side 100d, the operation state is shown in the air diagram by taking the case where the dry bulb temperature is T0 [° C.] and the relative humidity is φ0 [%] as an example.

In FIG. 2, the air conditioner includes an adsorbing means 10 and a refrigeration means 20. The refrigeration means 20 is filled with R404A, which is an HFC (hydrofluorocarbon) -based refrigerant, and includes a compressor 20a, a condenser 20b, an expansion valve 20c, which is a throttling device, an evaporator 20d, and piping connecting them. , Is composed of. The refrigerant may be R134a, R407C, R410A, natural refrigerant, or the like.
In addition, a first relative humidity sensor 31 is provided on the exit side of the first air 9d that has passed through the condenser 20b, and a second relative humidity sensor 32 is provided on the entry side of the second air 9a that enters the evaporator 20d. Yes.

(Desiccant rotor)
The moisture adsorbing means 10 includes a desiccant rotor 1, a motor 8 that is a driving means for moving the desiccant rotor 1, and first air 9 d that is supplied to the desiccant rotor 1 with first air 9 d that is air on the outside air side 100 d. A first fan 7d that is a means, and a second fan 7a that is a second air blowing means for supplying the second air 9a that is the air in the refrigerator compartment side 100a that is the second air-conditioned space to the desiccant rotor 1. .

Therefore, on the outside air side 100d, the first fan 7d rotates, whereby the first air 9d exchanges heat with the condenser 20b, and an airflow passing through the desiccant rotor 1 is formed. Moreover, in the refrigerator compartment side 100a, the 2nd air 7a passes the desiccant rotor 1 by the 2nd fan 7a rotating, and the airflow which heat-exchanges with the evaporator 20d is formed.
The desiccant rotor 1 has a cylindrical shape and is rotated in the direction of the arrow by the motor 8 to move between the outside air side 100d and the refrigerator compartment side 100a in a predetermined time (see FIG. 3).

(Moisture adsorption characteristics)
FIG. 5 shows the moisture adsorption characteristics of the solid adsorbent provided in the desiccant rotor 1 which is the moisture adsorbing means which is the main configuration of the air-conditioning apparatus according to Embodiment 1 of the present invention. The solid adsorbent is a porous silicon material provided with many pores of about 1.5 nm (nanometers).
In FIG. 5, the horizontal axis represents the relative humidity of the conditioned space, and the vertical axis represents the equilibrium adsorption amount of moisture. As can be seen from FIG. 5, the solid adsorbent used in the present embodiment has a slope that is the rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of 30% to 40% relative humidity of less than 30% or 40%. It is larger than the slope, which is the rate of change of the equilibrium adsorption amount of moisture relative to the relative humidity in the range exceeding%. That is, the second relative humidity and the first relative humidity are 30% and 40%, respectively.
The first relative humidity and the second relative humidity can be increased or decreased by increasing or decreasing the pore diameter of the solid adsorbent.

(Operation of desiccant rotor)
FIG. 4 is an air diagram illustrating the operation of the air-conditioning apparatus according to Embodiment 1 of the present invention. 2 and 4, the state of the air before passing through the desiccant rotor 1 with respect to the second air 9a passing through the desiccant rotor 1 on the refrigerator side 100a side is the temperature Tai, the second air inlet side relative humidity φa1, and the desiccant. Let the relative humidity of the second air 9a immediately after passing through the rotor 1 be φa2.
Further, the state of the windward air of the condenser 20b relative to the first air 9d passing through the desiccant rotor 1 on the outdoor air side 100d is relative to the first air 9d immediately after the dry bulb temperature T0, the relative humidity φ0, and the heat exchange. The humidity is φd1, and the first air outlet side relative humidity φd2 of the first air 9d immediately after passing through the desiccant rotor 1 is assumed.

(adsorption)
First, the operation in which the desiccant rotor 1 adsorbs moisture in the refrigerator compartment side 100a will be described.
The second air 9a is supplied to the desiccant rotor 1 and dehumidified from the second air inlet side relative humidity φa1 to φa2 along the isoenthalpy line. And after returning to the evaporator 20d and being cooled, it returns to the refrigerator compartment space. On the other hand, the desiccant rotor 1 adsorbs the moisture contained in the second air 9a (same as absorption).
At this time, in the refrigerating room side 100a, a control means (not shown) causes the second air outlet side relative humidity φa2 of the desiccant rotor 1 to be around 30% relative humidity based on the detection result of the second relative humidity sensor 32. The air volume of the second fan 7a is controlled, that is, the rotation speed is changed or the rotation is started and stopped.

  For example, when the second air outlet side relative humidity φa2 is 20% or less, the humidity is excessively reduced. Therefore, the air volume is increased until the relative humidity rises to around 30% to increase the dehumidification amount. it can. On the other hand, when the second air outlet-side relative humidity φa2 is 30% or more, dehumidification is insufficient. Therefore, the air volume is reduced until the relative humidity drops to around 30%, and the second fan 7a Input can be reduced. That is, since the air volume is not increased more than necessary, the input of the second fan 7a is reduced.

(Desorption)
On the outside air side 100d, a control means (not shown) controls the first fan 7d based on the detection result of the first relative humidity sensor 31 so that the first air inlet side relative humidity φd1 of the desiccant rotor 1 is around 30% relative humidity. The air volume is controlled, that is, the rotation speed is changed or the rotation is started and stopped.
For example, when the first air inlet side relative humidity φd1 of the desiccant rotor 1 is 20% or less, it is excessively dehumidified (corresponding to a temperature rise), and therefore the relative humidity rises to around 30%. Therefore, the heat exchange performance of the condenser 20b is increased and the input of the compressor 20a is decreased. On the other hand, if the first air inlet side relative humidity φd1 is 30% or more, the dehumidification is insufficient (corresponding to insufficient temperature rise), so the air volume is reduced until the relative humidity drops to around 30%. Thus, the input of the second fan 7a is reduced.

  As described above, the air volume is controlled by the first relative humidity sensor 31 and the second relative humidity sensor 32, and the second air outlet side relative humidity φa2 on the adsorption side and the first air inlet side relative humidity φd1 on the desorption side are set to a predetermined relative humidity. Therefore, as shown in FIG. 6, the solid adsorbent provided in the desiccant rotor 1 can maximize the amount of moisture adsorption and desorption.

  As described above, according to the present invention, the adsorption means 10 (desiccant rotor 1) removes latent heat, the cooling means (refrigeration cycle 20) removes sensible heat, and the regeneration (desorption) of the moisture adsorption means condenses in the refrigeration cycle 20. Covering with waste heat can greatly improve the capacity of the system.

[Embodiment 2]
6 and 7 are a schematic diagram for explaining the configuration of the air-conditioning apparatus according to Embodiment 2 of the present invention, and a schematic diagram for explaining the driving state of the moisture adsorbing means that is the main configuration of the air-conditioning apparatus. The second embodiment is different from the first embodiment (FIG. 2) in that an electric heater 70 is provided between the condenser 20b and the desiccant rotor 1, and the other parts are the same. The same reference numerals are given to the same parts, and a part of the description is omitted. 6 and 7, the air state of the space on the refrigerator compartment side 100a of the refrigerator warehouse is that the dry bulb temperature is Tai [° C.] and the second air inlet side relative humidity φa is 1%. The air condition on the outside air side 100d is that the dry bulb temperature is T0 [° C.] and the relative humidity is φ0% (see FIG. 7).

(Operation of desiccant rotor)
Next, the operation will be described. Since the operation of the second air 9a on the refrigerator compartment side 100a and the operation of the second fan 7a and the evaporator 20d are the same as those in the first embodiment, the operation (desorption) of the outside air side 100d having different operations is performed. Will be described. On the outside air side 100d, the first relative humidity φd1 of the desiccant rotor 1 is detected by the first relative humidity sensor 31, and the control means (not shown) controls the first fan 7d so that the relative humidity at that position is around 30%. The air volume and the electric heater 70 are controlled.

(Desorption)
For example, on the outside air side 100d, when the first air inlet side relative humidity φd1 of the desiccant rotor 1 is 20% or less, the first air 9d is excessively dehumidified, so that the air volume is increased as described above. Since the auxiliary heating by the electric heater 70 is not required, it is turned off. Thereby, the heat exchange performance of the condenser 20b improves and the input of the compressor 20a falls.
On the other hand, in the outdoor air side 100d, when the relative humidity φ0 is high and the first air inlet side relative humidity φd1 is 30% or more even after passing through the condenser 20b, the dehumidification is insufficient (corresponding to insufficient heating). However, if the air flow is lower than the predetermined air flow, the electric heater 70 is energized to increase the temperature of the first air, and the first air inlet side relative humidity φd1 is controlled to decrease to around 30%. .

  That is, the present invention has the same effects as those of the first embodiment, and by such control, it is possible to prevent the efficiency of the refrigeration means 20 from being reduced due to an excessive decrease in the air volume and to increase the desorption amount. There is.

[Embodiment 3]
8 and 9 are a schematic diagram for explaining the configuration of the air-conditioning apparatus according to Embodiment 3 of the present invention, and a schematic diagram for explaining the driving state of the moisture adsorbing means that is the main configuration of the air-conditioning apparatus. In the third embodiment, the third relative humidity sensor 33 and the first temperature sensor 39 are provided on the inlet side of the desiccant rotor 1 of the second air 9a in the refrigerator compartment side 100a. Unlike the first embodiment (FIG. 2), the other parts are the same, so the same parts are denoted by the same reference numerals and a part of the description is omitted. 8 and 9, the air condition of the space on the refrigerator compartment side 100a of the refrigerator warehouse is that the dry bulb temperature is Tai [° C.] and the second air inlet side relative humidity φa is 1%. The air condition on the outside air side 100d is that the dry bulb temperature is T0 [° C.] and the relative humidity is φ0%.

(Operation of desiccant rotor)
Next, the operation will be described based on FIG. 9 (air diagram explaining the operation of the air conditioner).
With respect to the second air 9a passing through the desiccant rotor 1 on the refrigerator compartment side 100a (adsorption side), the air state before passing through the desiccant rotor 1 is the temperature Tai and the second air inlet side relative humidity φa1, and the desiccant rotor 1 The air state immediately after passing through is the second air exit side relative humidity φa2.
On the other hand, with respect to the first air 9a passing through the desiccant rotor 1 on the outdoor air side 100d (desorption side), the air state on the windward side of the condenser 20b is set to the dry bulb temperature T0 and the relative humidity φ0, and passes through the condenser 20b. The air condition immediately after (the same as immediately after heat exchange) has the first air inlet side relative humidity φd1, and the air condition immediately after passing through the desiccant rotor 1 is the first air outlet relative humidity φd2. The air temperature when the first air inlet side relative humidity φd1 is 30% is set to “Td30”.

(adsorption)
First, the operation in which the desiccant rotor 1 adsorbs moisture in the refrigerator compartment side 100a will be described.
The second air 9a is supplied to the desiccant rotor 1, is dehumidified from the second air inlet side relative humidity φa1 to φa2 along the isoenthalpy line, flows into the evaporator 20d, and is cooled, and then is stored in the refrigerator compartment space. Return to. At this time, the second air outlet-side relative humidity φa2 of the desiccant rotor 1 is detected by the second relative humidity sensor 32, and the air volume of the second fan 7a is controlled so that the relative humidity is around 30%.

Further, the air temperature Tai detected by the first temperature sensor 39, the relative humidity φa2 detected by the second relative humidity sensor 32, the second air inlet side relative humidity φa1 detected by the third relative humidity sensor 33, and the second fan 7a. The amount of water Wa adsorbed by the desiccant rotor 1 is calculated by the following equation using the operating air volume Va.
Wa = f (Tai, φa1, φa2, Va)

(Desorption)
Next, desorption will be described. When the adsorbed water amount Wa calculated by the above equation is smaller than a predetermined value, for example, when the adsorbed amount Wa of the desiccant rotor 1 is small because the second air 9a is dry, the amount to be desorbed on the outside air side 100d is also Therefore, the first air inlet side relative humidity φd1 of the desiccant rotor 1 can be made higher than 30%. That is, the desiccant rotor 1 is desorbed within a range where the characteristic of the equilibrium adsorption amount changes rapidly between the second relative humidity 30% and the first relative humidity 40% (see FIG. 5).

  For example, a control device (not shown) controls to increase the air volume of the first fan 7d so that the first air inlet side relative humidity φd1 is 35%. Thereby, in the outdoor air side 100d, the temperature of the 1st air in the entrance side of the desiccant rotor 1 can be made low compared with the case where the 1st air entrance side relative humidity (phi) d1 is set to 30% (Td30-> Tdi, an air state) Tdi, φd1). For this reason, since the air volume of the 1st fan 7d of the desiccant rotor 1 increases, the heat exchange performance of the condenser 20b improves and the input of the compressor 20a falls.

In the third embodiment, the air temperature Tai detected by the first temperature sensor 39, the second air inlet side relative humidity φa1 detected by the third relative humidity sensor 33, and the second air detected by the first relative humidity sensor 31 are emitted. The moisture amount Wa adsorbed by the desiccant rotor 1 is calculated from the side humidity φa2 and the operating air volume Va of the second fan 7a, and the first air inlet side of the desiccant rotor 1 on the outside air side 100d (desorption side) based on the amount Although what controlled relative humidity (phi) d1 was demonstrated, this invention is not limited to this.
For example, the same applies when the difference between the second air inlet side relative humidity φa1 detected by the third relative humidity sensor 33 on the refrigerator side 100a (adsorption side) and the set relative humidity φs is equal to or less than a predetermined value. The same effect can be expected even if this control is performed.

[Embodiment 4]
(Desiccant rotor)
FIG. 10 is a schematic perspective view illustrating the configuration of the desiccant rotor installed in the air-conditioning apparatus according to Embodiment 4 of the present invention. In FIG. 10, the desiccant rotor 2 can be installed in any of the first to third embodiments described above, and the inlet duct 40 and the outlet duct 50 are installed on both sides of the desiccant rotor main body 60. ing. Note that the entry side or the exit side is referred to for convenience on the basis of the second air (adsorption side), and is opposite to the first air (desorption side).

The inlet duct 40 includes a cylindrical inlet cylinder 41, a first air passage through which the first air 9d circulates and a second air passage through which the second air 9a circulates by rotating inside the inlet cylinder 41. It has the entrance side partition plate 42 which partitions off (refer FIG.10 (b)). The outlet duct 50 includes a cylindrical outlet cylinder 51, a first air passage through which the first air 9d circulates and a second air passage through which the second air 9a circulates by rotating inside the outlet cylinder 51. And an exit side partition plate 52 (see FIG. 10C).
And the entrance side partition plate 42 and the exit side partition plate 52 are connected by a connection shaft (not shown) that penetrates the desiccant rotor main body 60, and rotate at the same phase. Therefore, the adsorption side area (same as the refrigeration room side 100a) and the desorption side area (same as the outside air side 100d) of the desiccant rotor main body 60 can be changed, so that the degree of freedom of control increases and the refrigeration room side 100a. The relative humidity can be quickly reached the set relative humidity.

(Operation of desiccant rotor)
Next, the operation of the desiccant rotor configured as described above will be described. On the outside air side 100d, the first air inlet side relative humidity φd1 of the desiccant rotor 2 is detected by the first relative humidity sensor 31, and the input side is determined by the difference between the detected first air inlet side relative humidity φd1 and the set relative humidity φs. The partition plate 42 and the outlet partition plate 52 are controlled to change the area of the first air passage and the area of the second air passage.

For example, when the outside air side 100d is dried and the difference between the detected first air inlet side relative humidity φd1 and the set relative humidity φs is large, a larger amount of desorption (regeneration) is possible on the outside air side 100d. It is possible to increase the amount of adsorption by that amount. That is, the entrance side partition plate 42 and the exit side partition plate 52 are rotated to increase the area of the second air passage, and the amount of moisture adsorption can be increased by the amount of the increase in the adsorption side area.
At this time, on the outside air side 100d, the area of the first air passage is reduced, and the area of the desorption side is reduced. However, the second air outlet side relative humidity φa2 of the desiccant rotor 2 is detected by the first relative humidity sensor 31. The air volume of the first fan 7d is controlled so that the detected relative humidity is around 30%.

Therefore, the dehumidification of the refrigerator compartment side 100a can be strengthened, the relative humidity can be set to the set value in a short time, and the air volume of the first fan 7d is appropriately controlled. It is possible to prevent a decrease in efficiency and maintain a predetermined desorption amount (same as the adsorption amount).
In the case where the air conditioner includes the electric heater 70, when the area of the second air passage is enlarged on the refrigerator compartment side 100a and the air volume of the second fan 7a is increased, the electric heater 70 on the outdoor air side 100d. May be controlled so that the first air inlet side relative humidity φd1 is in the vicinity of 30%.

  As is clear from the above description, the desiccant rotor 2 of the fourth embodiment can be used as the desiccant rotor 1 in the first to third embodiments, and the effects in the first to third embodiments described above are obtained by such use. Is further promoted.

Fig. 4 is a moisture equilibrium adsorption characteristic diagram of a conventional zeolite. Schematic explaining the structure of the air conditioning apparatus which concerns on Embodiment 1 of this invention. The schematic diagram of the desiccant rotor of the air conditioning apparatus which concerns on Embodiment 1 of this invention. Schematic explaining the drive state of the water | moisture-content adsorption | suction means of the air conditioning apparatus shown in FIG. FIG. 3 is a moisture adsorption characteristic diagram of a solid adsorbent provided in the desiccant rotor 1 shown in FIG. 2. Schematic explaining the structure of the air conditioning apparatus which concerns on Embodiment 2 of this invention. Schematic explaining the drive state of the water | moisture-content adsorption | suction means of the air conditioning apparatus shown in FIG. Schematic explaining the structure of the air conditioning apparatus which concerns on Embodiment 3 of this invention. Schematic explaining the drive state of the water | moisture-content adsorption | suction means of the air conditioning apparatus shown in FIG. Schematic explaining the structure of the desiccant rotor which concerns on Embodiment 4 of this invention.

Explanation of symbols

1: desiccant rotor, 7a: second fan, 7d: first fan, 8: motor, 9a: second air, 9d: first air, 20: refrigeration means, 20a: compressor, 20b: condenser, 20c: Expansion valve, 20d: evaporator, 31: first relative humidity sensor, 32: second relative humidity sensor, 33: third relative humidity sensor, 39: first temperature sensor, 40: inlet duct, 41: inlet cylinder , 42: inlet side partition plate, 50: outlet side duct, 51: outlet side cylinder, 52: outlet side partition plate, 60: desiccant rotor body, 70: electric heater, φ0: outside relative humidity, φa1: second air Input side relative humidity (adsorption side), φa2: second air output side relative humidity (adsorption side), φd1: first air input side relative humidity (desorption side), φd2: first air output side relative humidity (desorption side) , Φs: set relative humidity, 100d: outside air side, 100a: cold Storage room side, Va: operating air volume, Wa: adsorbed water content.

Claims (5)

The rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity is the relative humidity outside the range of the relative humidity. A moisture adsorbing means that is greater than the rate of change of the equilibrium adsorption amount with respect to and the first relative humidity and the second relative humidity are in the range of 30% to 40%;
Second air blowing means for supplying second air to which moisture is adsorbed by the moisture adsorption means;
First blowing means for supplying first air for desorbing moisture adsorbed on the moisture adsorbing means;
Driving means for driving the moisture adsorbing means to change a region to which the first air and the second air are supplied;
A refrigerant circuit that includes a compressor that is filled with refrigerant and compresses the refrigerant, a condenser that exchanges heat with the first air, a throttling device that expands the refrigerant, and an evaporator that exchanges heat with the second air;
Control means for controlling the supply amount of at least one or both of the first air and the second air ,
A first relative humidity sensor that detects the relative humidity of the first air that is disposed between the condenser and the moisture adsorption means, the condenser being disposed on the windward side of the first air with respect to the moisture adsorption means. When,
The second relative humidity is configured such that the evaporator is arranged on the leeward side of the second air with respect to the moisture adsorbing means, and detects the relative humidity of the second air installed between the evaporator and the moisture adsorbing means. A sensor, and
The air conditioner characterized in that the control means controls each of the first air blowing means and the second air blowing means based on detection results of the first relative humidity sensor and the second relative humidity sensor . Having a heater between the condenser and the moisture desorption means;
The control means controls the first air blowing means, the second air blowing means, and the heater based on detection results of the first relative humidity sensor and the second relative humidity sensor. air conditioning system. A third relative humidity sensor for detecting an air relative humidity at the inlet of the moisture adsorbing means;
The control means controls to control the first air blowing means and the second air blowing means based on detection results of the first relative humidity sensor, the second relative humidity sensor, and the third relative humidity sensor. The air conditioning apparatus according to claim 1 . A heater between the condenser and the moisture desorption means, and a third relative humidity sensor for detecting the air relative humidity at the inlet of the moisture adsorption means,
The control means controls the first air blowing means, the second air blowing means, and the heater based on detection results of the first relative humidity sensor, the second relative humidity sensor, and the third relative humidity sensor. The air conditioning apparatus according to claim 1 . The said water | moisture-content adsorption | suction means has a passage area switching means which changes the ratio of the area of the 1st air passage through which the said 1st air passes, and the area of the 2nd air passage through which the said 2nd air passes. Item 5. The air conditioner according to any one of Items 1 to 4 .

Images