JP2003326126A - Compressed air dehumidifier - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressed air dehumidifier capable of reducing power consumption. <P>SOLUTION: The compressed air dehumidifier 1 is constituted so as to cool the air compressed by a compressor C to be introduced into a heat exchanger 2 by the secondary cooling part 12 in a refrigeration cycle 3 to condense moisture in air and equipped with a pressure feed amount variable compressor 22 capable of requlating the pressure feed amount of a gasified cooling medium to the condenser 23 of the refrigeration cycle 3, a temperature sensor TS for detecting the temperature of the air compressed by the compressor C and a control part 6 for controlling the compressor 22 on the basis of the temperature detected by the temperature sensor TS to regulate the refrigeration capacity of the refrigeration cycle 3. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to compressed air in a heat exchanger, which is cooled by an evaporator in a refrigerating cycle to condense moisture contained in the compressed air so as to be dehumidified. The present invention relates to a dehumidifying device.

[0002]

2. Description of the Related Art As a compressed air dehumidifier of this type, FIG.
The dehumidifying device 51 shown in (1) is conventionally known. This dehumidifier 51 is an air compressor (see FIG. 3.
(Also referred to as "compressor") heat exchanger 2 that dehumidifies the moisture contained in the compressed air sent by C to dew
And a refrigeration cycle 5 for cooling compressed air in the heat exchanger 2.
3 and 3. In this case, the heat exchanger 2 has the inlet 2
The compressed air introduced from a is configured to be able to be discharged from the discharge port 2b through a gas flow path including the primary cooling unit 11, the secondary cooling unit 12, and the reheating unit 13. Also, the heat exchanger 2
A drain trap 9 for draining moisture generated by dehumidification to the outside is attached to each of the drain ports 2c and 2d. On the other hand, the refrigeration cycle 53 is provided in the secondary cooling unit 12 of the heat exchanger 2, and an evaporator 21 that cools the compressed air by the heat of vaporization of the refrigerant, and a compressor that pumps the vaporized refrigerant with a constant pumping capacity. A machine 62, a condenser 23 for condensing (liquefying) the compressed vaporized refrigerant, a liquid receiver 24 for temporarily storing the liquefied refrigerant, and a capillary tube 65 for depressurizing the liquefied refrigerant. This dehumidifier 51
As shown in FIG. 3, for example, is installed in the room ID1 (machine room) of the building R1 together with the compressor C.

In the dehumidifying device 51, first, the compressor 62
Is driven to circulate the refrigerant in the refrigeration cycle 53. At this time, the liquefied refrigerant in the liquid receiver 24 passes through the capillary tube 65 and is discharged into the evaporator 21, and the discharged liquefied refrigerant is vaporized in the evaporator 21, so that the heat of vaporization causes heat exchange. Secondary cooling unit 1 of container 2
2 is cooled. Next, by driving the compressor C in this state, compressed air containing water is introduced into the heat exchanger 2 from the inlet 2a via the duct D1 (see FIG. 3). At this time, the compressed air introduced into the heat exchanger 2 is pre-cooled when passing through the primary cooling unit 11,
Next, when passing through the secondary cooling unit 12, the evaporator 21 cools the dew point temperature or lower. As a result, the water in the compressed air is condensed as dew condensation water on the surfaces of the fins attached to the evaporator 21, and this dew condensation water flows down toward the bottom of the heat exchanger 2 to drain the drain trap 9 from the drain port 2c.
And then discharged to the outside.

On the other hand, when the compressed air dehumidified in the secondary cooling section 12 passes through the reheating section 13, it is reheated by the compressed air introduced from the inlet 2a and then discharged from the outlet 2b. To be done. After this, as shown in FIG.
Compressed air dehumidified by 1 is the indoor ID of building R2
It is supplied to the supply object X (for example, various air tools) installed in No. 2 via the duct D2. In this case, when the dehumidification of the compressed air by the dehumidifier 51 is incomplete,
For example, in the winter when the outdoor OD is relatively low in temperature, moisture remaining in the compressed air after dehumidification is condensed as condensed water in the duct D2, and this condensed water is supplied to the supply target X together with the compressed air. . Therefore, in the conventional dehumidifying device 51, in order to reliably dehumidify the compressed air that has been pressure-fed by the compressor C, the compressor 62 that is capable of pressure-feeding sufficient refrigerant to cool the secondary cooling unit 12 to the dew point temperature. It regulates the pumping ability of the. As a result, even if the outdoor OD is cold in winter, dew condensation in the duct D2 is avoided.

[0005]

However, the conventional dehumidifier 51 has the following problems to be improved. That is, as described above, when the compressed air is cooled to a temperature equal to or lower than the dew point temperature between the time when the compressed air is compressed by the compressor C and the time when the compressed air is supplied to the supply target X, the moisture in the compressed air condenses, Condensation water mixes with compressed air. Therefore, in order to prevent dew condensation water from mixing into the compressed air, it is necessary to cool the decompressed air to a dew point temperature that does not cause dew condensation water in the duct D2 or the like throughout the four seasons. Therefore, in the conventional dehumidifying device 51, when decompressing the compressed air, the compressor 62 of the refrigeration cycle 53 is secondarily cooled to a temperature equal to or lower than the target dew point temperature at which the compressed air can be dehumidified to the extent that dew condensation water is not generated in the duct D2 or the like. It is constantly operated with a constant pumping capacity capable of pumping a sufficient amount of refrigerant to keep the inside of the cooling unit 12. In this case, the temperature of the outdoor OD becomes relatively high, and the dehumidifier 5 is used in summer when the amount of water contained in the air is large.
Even if the compressed air after dehumidification by No. 1 contains some moisture, the compressed air is duct D2 because the outside air temperature is high.
It is not cooled in the interior or the like until the dew point temperature is reached, and the moisture in the compressed air is not condensed in the duct D2 or the supply target X. Therefore, even in the summer or the like, even if the secondary cooling unit 12 is not cooled to the target dew point temperature that is substantially equal to the outside air temperature in winter, or the target dew point temperature that does not cause dew condensation water in the duct D2 or the like throughout the four seasons, the dew condensation water is compressed. Since it is not supplied to the supply object X together with the air, no harmful effect actually occurs.

However, in the conventional dehumidifier 51, in order to prevent dew condensation in the duct D2 in winter, the secondary cooling unit 12 reaches a target dew point temperature at which dew condensation water does not occur in the duct D2 even in winter. Compressor 6 with the ability to pump
2 is always operating. Therefore, in summer and the like, the secondary cooling unit 12 is cooled more than necessary, and a large amount of moisture contained in the atmosphere is condensed, so that not only the cooling load of the compressed air increases but also low temperature Since the amount of water condensed by increasing the amount of water to be condensed increases, the load due to the latent heat of condensation also increases, resulting in the problem of consuming more power than necessary. Further, in the conventional dehumidifier 51, the compressor 62 is constantly operated with a constant pumping capacity so that the secondary cooling unit 12 cools the compressed air to a target dew point temperature that does not cause dew condensation in the duct D2 or the like throughout the four seasons. And maintained to dehumidify. For this reason, the compressed air discharged from the discharge port 2b also has a relatively low temperature. As a result, in the summer when the outdoor OD is at a high temperature, moisture in the atmosphere is condensed on the outer surface of the duct D2 to cool it more than necessary. There is also a problem that the energy spent for doing so is released into the atmosphere.

The present invention has been made in view of such problems to be improved, and a main object of the present invention is to provide a compressed air dehumidifying device capable of reducing power consumption.

[0008]

In order to achieve the above object, a compressed air dehumidifying apparatus according to the present invention cools air compressed by an air compressor and introduced into a heat exchanger by an evaporator in a refrigeration cycle. A compressed air dehumidifying device that dehumidifies the water in the air by dew condensation, which is a variable pressure feed amount refrigerant compression means capable of adjusting the pressure feed amount of the vaporized refrigerant to the condenser of the refrigeration cycle,
Temperature detection means for detecting the temperature of the air compressed by the air compressor, and a control section for controlling the refrigerant compression means on the basis of the temperature detected by the temperature detection means to adjust the refrigerating capacity of the refrigeration cycle. It has and.

In this case, the refrigerant compression means comprises an inverter control type refrigerant compressor, and the control section controls the operating state of the refrigerant compressor to adjust the pumping capacity of the refrigerant compression means. Preferably.

Further, the refrigerant compressing means comprises a plurality of refrigerant compressors, and the control section individually controls the driving of each of the refrigerant compressors to adjust the pressure feeding capacity of the refrigerant compressing means. Is preferred.

Further, the temperature detecting means is provided with a storage unit for storing temperature difference information about a temperature difference between a room temperature at a place where the compressed air dehumidifier is installed and a temperature of air compressed by the air compressor. A temperature sensor that detects the room temperature; and a calculator that calculates the temperature of the compressed air based on the room temperature detected by the temperature sensor and the temperature difference information stored in the storage unit. It is preferable that the control section controls the refrigerant compression means based on the temperature calculated by the calculation section.

Further, an operation unit configured to be capable of inputting differential temperature correction information for correcting the differential temperature information stored in the storage unit is provided, and the control unit inputs the differential temperature correction information via the operation unit. It is preferable that the temperature difference information stored in the storage unit is corrected based on the temperature difference correction information, and the corrected temperature difference information is stored in the storage unit as the new temperature difference information.

Further, it is preferable that the control section adjusts the pressure feeding capacity of the refrigerant compression means stepwise based on the temperature detected by the temperature detection means.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of the compressed air dehumidifying device according to the present invention will be described below with reference to the accompanying drawings. The same components as those of the conventional dehumidifying device 51 are designated by the same reference numerals, and duplicate description will be omitted.

First, the structure of the dehumidifier 1 will be described with reference to FIG.
Will be described with reference to.

As shown in the figure, the dehumidifier 1 comprises a heat exchanger 2, a refrigeration cycle 3, an inverter 4, a storage unit 5, a control unit 6, an operating unit 7 and a temperature sensor TS. In this case, the temperature sensor TS constitutes the temperature detection means in the present invention together with the control unit 6, and as an example, the dehumidifier 1 and the compressor C together with the building R.
It is installed in the first indoor ID1, detects the room temperature of the indoor ID1, and outputs the detection signal S regarding the detected temperature. On the other hand, the heat exchanger 2 is formed in a cylindrical shape as a whole, and has an inlet 2a for introducing compressed air and an outlet 2b for discharging dehumidified compressed air. In this case, as shown in FIG. 3, the inlet 2a of the heat exchanger 2 has
The compressor C is connected via the duct D1, and the supply object X is connected to the discharge port 2b via the duct D2.

As shown in FIG. 1, the refrigeration cycle 3 includes an evaporator 21, a refrigerant compressor 22, a condenser 23, a liquid receiver 24 and an electronic expansion valve 25. The evaporator 21 is arranged in the secondary cooling unit 12 of the heat exchanger 2 and cools the compressed air by the heat of vaporization of the refrigerant. The refrigerant compressor (hereinafter, also referred to as “compressor”) 22 corresponds to the refrigerant compression means in the present invention, and is composed of a variable-pressure-feed-rate compressor capable of linearly variably controlling the pressure-feeding capacity of the refrigerant. Specifically, the dehumidifying apparatus 1 employs an inverter control type compressor that varies the amount of pumping in multiple stages according to the output of the inverter supplied by the inverter 4. This compressor 2
The inverter 2 is supplied with an inverter output by the inverter 4 under the control of the control unit 6 to pump the vaporized refrigerant with a predetermined pumping capacity to circulate the refrigerant in the refrigeration cycle 3. The electronic expansion valve 25 controls the evaporator 21 under the control of the controller 6.
The flow rate of the liquefied refrigerant discharged inside is adjusted. The inverter 4 supplies an inverter output to the compressor 22 under the control of the control unit 6. The storage unit 5 stores room temperature of indoor ID 1 and outdoor O
The temperature difference data Dt (“temperature difference information” in the present invention) regarding the temperature difference with the temperature of D (that is, the temperature of the portion through which the duct D2 passes) and the control data Dp for controlling the inverter 4 are stored. .

The temperature difference data Dt is generated according to the installation environment of the dehumidifying device 1 and stored in the storage unit 5 prior to the start of use. In this case, the temperature difference between the room temperature of the indoor ID 1 and the temperature of the outdoor OD differs depending on the installation environment of the dehumidifier 1. Specifically, for example, when the building R1 where the dehumidifying device 1 is installed is relatively narrow and a plurality of devices are installed together with the dehumidifying device 1 and the compressor C, the dehumidifying device 1, the compressor C and various devices are installed. Due to the heat generation, the temperature of the indoor ID1 rises more than the outdoor OD. Further, for example, when the building R1 is relatively large and there is no heat generating device other than the dehumidifying device 1 and the compressor C, the dehumidifying device 1 and the compressor are the factors that raise the room temperature of the indoor ID1 with respect to the temperature of the outdoor OD. Since only C has a small effect on the rise in room temperature, the temperature of the indoor ID1 is almost the same as the outdoor OD. In this way, since the temperature difference between the room temperature of the indoor ID 1 and the temperature of the outdoor OD differs depending on the installation environment of the dehumidifier 1, the temperature difference data Dt corresponding to the installation environment is generated and stored in the storage unit 5. In the dehumidifying device 1, the temperature difference data Dt generated based on the general relationship between the room temperature and the outside temperature is stored as the initial value. Therefore, as will be described later, the differential temperature data Dt as an initial value
Is corrected according to the installation environment, the temperature difference data Dt suitable for the installation environment is generated and stored in the storage unit 5.

On the other hand, the control data Dp is composed of data for controlling the operating state of the compressor 22 via the inverter 4 according to the temperature of the outdoor OD. In this case, the operating state of the compressor 22 can be changed steplessly or in multiple steps corresponding to the temperature of the outdoor OD, but the control becomes relatively complicated. Therefore, in this dehumidifying device 1,
The outdoor OD is controlled in two stages when the temperature is low and when it is high. Specifically, the control data Dp is, for example,
When the temperature of the outdoor OD is less than 20 ° C, the secondary cooling unit 1
When the temperature of the outdoor OD is 20 ° C. or higher, the secondary cooling unit 12 is operated when the compressor 22 is operated with a pumping capacity capable of pumping a sufficient amount of refrigerant to cool 2 to the dew point temperature (10 ° C. as an example). A temperature slightly higher than the dew point temperature (for example, 1
It is composed of data indicating that the compressor 22 is operated with a pumping capacity capable of pumping a sufficient amount of refrigerant to cool it to 5 ° C.).

The control unit 6 functions as a calculation unit of the temperature detecting means of the present invention and a control unit of the present invention, and stores a detection signal S (room temperature of the room ID1) output by the temperature sensor TS and a memory. The temperature of the outdoor OD is calculated on the basis of the temperature difference data Dt stored in the unit 5, and the inverter 4 is controlled according to the calculation result, so that the compressor 22 has a capability of pumping the refrigerant (ie, refrigeration). The refrigerating capacity of cycle 3) is regulated and controlled. In this case, the control unit 6 actually adjusts and controls the refrigerant pumping capacity of the compressor 22 according to the operating state of the compressor C (that is, the flow rate of the compressed air pumped to the heat exchanger 2). In the embodiments of the present invention, in order to facilitate understanding of the present invention, the description of the configuration and the operation regarding the adjustment control of the refrigerant pumping capacity according to the compressed air amount will be omitted. The operation unit 7 is configured by arranging various switches for inputting various information (“differential temperature correction information” in the present invention) for correcting the differential temperature data Dt stored in the storage unit 5 according to the installation environment. Has been done.

Next, a dehumidifying method for the compressed air by the dehumidifying device 1 will be specifically described with reference to the drawings.

When using the dehumidifying apparatus 1, first,
The temperature difference data Dt as an initial value stored in the storage unit 5 is corrected according to the installation environment of the dehumidifier 1. Specifically, after the dehumidifier 1 and the compressor C are installed in the room ID1 of the building R1, the compressor C is driven to supply compressed air to the dehumidifier 1. After operating the compressor C for a while in this state, the operation unit 7 is operated to cause the control unit 6 to execute a correction process for correcting the temperature difference data Dt. In this correction process, the control unit 6 first acquires the room temperature of the indoor ID 1 and the temperature of the outdoor OD, respectively. At this time, the control unit 6 calculates the room temperature of the room ID1 based on the detection signal S of the temperature sensor TS. Regarding the temperature of the outdoor OD, for example, after the operator measures the outside air temperature using a thermometer,
Input to the dehumidifier 1 via the operation unit 7.

Next, the control unit 6 informs the operator of the current season (in this case, as an example, 1
Request to enter information about which month of the two months it belongs to). In this case, as shown in FIG. 2, the temperature differences t1 and t2 between the temperature of the outdoor OD and the room temperature of the indoor ID1 are O
There is a difference between summer when the temperature of D is high and winter when the temperature of the outdoor OD is low. Therefore, when the temperature of the outdoor OD is calculated by adding the temperature difference of the same value to the room temperature of the room ID1 measured through the temperature sensor TS throughout the four seasons, it depends on the difference in the amount of water contained in the air. The calculation result may differ from the actual temperature due to the change in the heat generation amount of the compressor C and the influence of the sunshine condition. Therefore, in the dehumidifier 1, the difference between the calculation result and the actual temperature is reduced throughout the four seasons by using the temperature difference data Dt that describes the temperature difference that differs for each month. Therefore, when correcting the temperature difference data Dt, the control unit 6 specifies the “month” at the time of performing the correction based on the information regarding the “month” input by the operator, and specifies the specified “month”.
Correct the temperature difference for.

Specifically, the control unit 6 controls the temperature sensor TS.
Room temperature of the indoor ID 1 calculated based on the detection signal S output by the outdoor OD input via the operation unit 7.
Calculate the temperature difference from the temperature. At this time, if the calculation result is different from the temperature difference corresponding to the temperature difference data Dt stored in the storage unit 5, the temperature difference data Dt is corrected. This completes the temperature difference correction process for the "month" input by the operator. Next, the control unit 6 corrects the differential temperature for the other 11 months by adding / subtracting to / from the calculated differential temperature based on a predetermined monthly change rate. As a result, the correction of the temperature difference for 12 months is completed, and the temperature difference data Dt that matches the installation environment of the dehumidifier 1 is stored in the storage unit. In addition, the above-described correction process needs to be performed only once when the dehumidifying device 1 is installed,
After the start of use, the temperature difference data Dt may be corrected when a new heat source (various devices other than the compressor C, etc.) is installed in the building R1.

On the other hand, in dehumidifying the compressed air, first,
The control unit 6 controls the inverter 4 according to the temperature of the outdoor OD to operate the compressor 22 with a predetermined pumping capacity. Specifically, the control unit 6 firstly determines the temperature sensor T.
The temperature of the outdoor OD is calculated based on the detection signal S output by S and the temperature difference data Dt stored in the storage unit 5. Next, the control unit 6 determines whether the calculation result (outdoor OD temperature) is 20 ° C. or higher. At this time, for example, in the winter when the temperature of the outdoor OD is low, the control unit 6
Determines that the calculation result is lower than 20 ° C., and controls the secondary cooling unit 12 to be lower than the target dew point temperature (this In this case, as an example, the inverter 4 is controlled so that the compressor 22 is operated with a pumping capacity capable of pumping a sufficient refrigerant to cool it to 10 ° C. In response to this, the inverter 4 outputs a predetermined inverter output to the compressor 2
Supply to 2. At this time, the compressor 22 is replaced by the evaporator 21.
The vaporized refrigerant therein is sucked and sequentially sent to the condenser 23 under pressure. Along with this, the liquefied refrigerant in the liquid receiver 24 is changed to the electronic expansion valve 25.
After being discharged to the inside of the evaporator 21 via the, it is expanded and vaporized inside the evaporator 21. As a result, the secondary cooling unit 12 is cooled to the target dew point temperature or lower.

Next, the compressor C is driven in this state. At this time, the compressor C sucks the air of the indoor ID 1 and sends it to the heat exchanger 2 under pressure. As a result, compressed air containing water is introduced into the heat exchanger 2 from the inlet 2a via the duct D1. At the same time, the air in the outdoor OD is sucked into the indoor ID1 through the intake holes VI (see FIG. 3) provided in the building R1. In this case, the compressed air introduced into the heat exchanger 2 is heated by the compressor C to 40 ° C. or higher. Next, the compressed air is pre-cooled when passing through the primary cooling unit 11, and when passing through the secondary cooling unit 12, the evaporator 21.
Is cooled to the target dew point temperature. At this time, the moisture in the compressed air is condensed as dew condensation water on the surfaces of the fins attached to the evaporator 21, and then flows down toward the bottom of the heat exchanger 2, and the heat exchanger 2 is discharged through the drainage port 2c. 2 is discharged to the outside. On the other hand, the compressed air that has been cooled to below the target dew point temperature in the secondary cooling unit 12 and has been substantially completely dehumidified, when passing through the reheating unit 13, removes the heat of the compressed air introduced from the introduction port 2 a. After being reheated by depriving it, it is discharged to the outside of the heat exchanger 2 through the discharge port 2b. After this,
As shown in FIG. 3, the compressed air dehumidified by the dehumidifier 1 is supplied to the supply object X installed in the indoor ID2 of the building R2 through the duct D2. In this case, since the compressed air passing through the duct D2 is almost completely dehumidified by the dehumidifying device 1, even if the outdoor OD is in the low temperature winter season, dew condensation in the duct D2 is avoided. As a result, the dehumidified compressed air is supplied to the supply object X.

On the other hand, when the temperature of the outdoor OD calculated based on the detection signal S output from the temperature sensor TS and the temperature difference data Dt is 20 ° C. or higher (in summer), the control unit 6
Is a refrigerant sufficient to cool the secondary cooling unit 12 to a temperature slightly higher than the target dew point temperature (15 ° C. in this case) that does not cause dew condensation water in the duct D2 or the like throughout the four seasons based on the control data Dp. The inverter 4 is controlled so that the compressor 22 is operated with a pumping capacity capable of pumping. In response to this, the inverter 4 supplies a predetermined inverter output to the compressor 22. As a result, the secondary cooling unit 12
Cool to 5 ° C. Next, by driving the compressor C, compressed air containing water is introduced into the heat exchanger 2 through the inlet 2a. In this case, the compressed air introduced into the heat exchanger 2 is cooled to 15 ° C. by the evaporator 21 when passing through the secondary cooling unit 12. At this time, the moisture in the compressed air is condensed as dew condensation water on the surfaces of the fins attached to the evaporator 21, and then flows down toward the bottom of the heat exchanger 2, and the heat exchanger 2 passes through the drain port 2c.
Is discharged from the outside. On the other hand, the compressed air dehumidified when passing through the secondary cooling unit 12 is discharged to the outside of the heat exchanger 2 from the discharge port 2b. Thereafter, as shown in FIG. 3, the compressed air dehumidified by the dehumidifying device 1 is supplied to the supply object X installed in the indoor ID2 of the building R2 through the duct D2.

In this case, the temperature in the secondary cooling section 12 is 15 ° C., which is slightly higher than the target dew point temperature at which the dew condensation water is not generated in the duct D2 or the like throughout the four seasons. Contains water. However, as described above, in the summer when the periphery of the duct D2 through which the compressed air passes (that is, the outdoor OD) and the periphery of the supply target object X are relatively high in temperature, the compressed air contains a slightly large amount of water. Even if it does, since this moisture does not condense in the duct D2, no harmful effect actually occurs. Therefore, the compressed air that has been sufficiently dehumidified to the extent that it does not affect use can be supplied to the supply target X. Note that the control unit 6 periodically (in this case, the temperature of the outdoor OD) based on the detection signal S output by the temperature sensor TS and the differential temperature data Dt when dehumidifying the compressed air by the dehumidifying device 1.
The calculation is performed at intervals of several minutes as an example, and the inverter 4 is controlled according to the calculation result. Therefore, as indicated by a point A in FIG. 3, when the temperature (calculation result) of the outdoor OD is lower than 20 ° C., the control unit 6 has a compressor with a pumping capacity capable of cooling the secondary cooling unit 12 to 10 ° C. The inverter 4 is controlled so that 22 operates. Further, as indicated by a point B in the figure, when the temperature (calculation result) of the outdoor OD becomes 20 ° C. or higher, the control unit 6 compresses the secondary cooling unit 12 with a pumping capacity capable of cooling to 15 ° C. The inverter 4 is controlled so that the machine 22 operates. As a result, even in the summer, compressed air is almost completely dehumidified when the temperature of the outdoor OD decreases, so that dew condensation in the duct D2 can be avoided.

As described above, according to the dehumidifying apparatus 1, the control unit 6 controls the pumping capacity (operating state) of the compressor 22 according to the temperature of the outdoor OD to adjust the refrigerating capacity of the refrigerating cycle 3. As a result, the compressor 22 can be used in summer (when the outdoor OD is hot) where it is not necessary to completely dehumidify the compressed air.
The power consumption can be sufficiently reduced. in this case,
When the temperature of the outdoor OD is low, the control unit 6 controls the inverter 4 to move the secondary cooling unit 12 to the duct D2 throughout the four seasons.
Even if the temperature of the outdoor OD is low in the winter, the duct D2 is operated by operating the compressor 22 with a pumping capacity capable of cooling to a target dew point temperature that does not generate dew condensation water in the inside or the like.
Condensation inside can be avoided. On the other hand, in the summer when the outdoor OD is hot, the secondary cooling unit 12 is cooled to 15 ° C., and therefore the secondary cooling unit 12 is cooled to a target dew point temperature that does not cause dew condensation in the duct D2 or the like throughout the four seasons during dehumidification. As a result of the temperature of the compressed air discharged from the heat exchanger 2 (compressed air after dehumidification) becoming higher than that in the case where it is done, dew condensation on the outer surface of the duct D2 can be avoided. Further, according to the dehumidifying device 1, since the compressor 22 of variable pumping amount (inverter control system) capable of adjusting the pumping amount of the vaporized refrigerant to the condenser 23 in the refrigeration cycle 3 is provided, the temperature of the outdoor OD is reduced. In addition to the change of the operating state according to the above, it is possible to finely adjust the pressure feeding capacity according to the amount of compressed air fed by the compressor C. Therefore, the power consumption of the compressor 22 can be further reduced, and the occurrence of dew condensation inside and outside the duct D2 can be avoided.

Further, according to the dehumidifying apparatus 1, the room temperature of the installation location (in this case, the indoor ID 1) and the temperature of the air sucked into the indoor ID 1 by the compressor C via the intake hole VI (that is, the outdoor OD) are detected. According to the temperature of the outdoor OD calculated by the control unit 6 based on the detection signal S output by the temperature sensor TS and the temperature difference data Dt, the memory unit 5 stores the temperature difference data Dt about the temperature difference Dt. By adjusting the pumping capacity of the compressor 22 (that is, the refrigerating capacity of the refrigerating cycle 3) by, for example, the temperature sensor TS
The temperature sensor TS can be easily installed and the signal cable for the temperature sensor TS can be easily routed as compared with the configuration in which the temperature sensor is directly measured by installing the temperature sensor on the outdoor OD. . In this case, the control unit 6 controls the inverter 4 according to the temperature of the outdoor OD calculated based on the room temperature of the indoor ID 1 and the temperature difference data Dt, so that the temperature of the outdoor OD is directly measured and the inverter 4 is measured.
The refrigerating capacity of the refrigerating cycle 3 (pressure feeding capacity of the compressor 22) can be appropriately adjusted in the same manner as the control method for controlling the.

Further, according to the dehumidifying device 1, the temperature difference correction information (outdoor O
The temperature difference data Dt stored in the storage unit 5 is corrected on the basis of the temperature information D)
By storing t in the storage unit 5 as new differential temperature data Dt, the refrigerating capacity of the refrigerating cycle 3 (in this case, the pumping capacity of the compressor 22) is appropriately adjusted according to the installation environment of the dehumidifying device 1. You can In addition, the control unit 6 is outdoors O
According to the temperature of D, the pumping capacity of the compressor 22 (that is, the refrigerating capacity of the refrigerating cycle 3) is adjusted to two stages (in this case, two stages of less than 20 ° C. and 20 ° C. or more, for example). As a result, the regulation control becomes easier as compared with a control method that regulates steplessly or in multiple stages,
Since it is not necessary to increase the processing capacity of the control unit, the manufacturing cost of the dehumidifying device 1 can be reduced accordingly. In this case, for example, even if the pumping capacity of the compressor 22 is adjusted in multiple stages (or steplessly) in a relatively short cycle, it takes some time for the inside of the secondary cooling unit 12 to fall or rise to the target temperature. Therefore, the multi-step adjustment in a relatively short cycle has no meaning in reality. Therefore, even if the dehumidification device 1 is adjusted in two stages or about three to five stages, the dew condensation inside and outside the duct D2 can be effectively avoided and the power consumption by the compressor 22 can be sufficiently increased. It can be reduced.

The present invention is not limited to the configurations shown in the above-mentioned embodiments of the present invention. For example, in the embodiment of the present invention, the example in which the inverter control type compressor 22 is adopted has been described, but the configuration of the variable-pressure-feed-type refrigerant compression means in the present invention is not limited to this. May be provided with a plurality of fixed compressors. Even with this configuration, by individually controlling the number of operating compressors, it is possible to adjust the pressure-feeding capacity of the refrigerant, that is, the refrigerating capacity of the refrigerating cycle 3, similarly to the dehumidifying device 1 described above. According to this configuration, the refrigerant compression unit can be configured at a relatively low cost, so that the manufacturing cost of the dehumidifying device 1 as a whole can be reduced. Further, in the embodiment of the present invention, an example in which the compressor C and the dehumidifying device 1 and the supply target X are installed at different installation locations (in this case, the buildings R1 and R2) has been described. The installation form of the device 1 is not limited to this, and the compressor C, the dehumidifying device 1, and the supply object X can be installed in one building. Further, in the embodiment of the present invention, an example in which the temperature sensor TS is installed in the indoor ID1 together with the heat exchanger 2 has been described, but the present invention is not limited to this, and the temperature sensor TS may be installed in the outdoor OD. Good. According to this configuration, it is possible to eliminate the calculation process related to the temperature of the outdoor OD based on the temperature difference data Dt, so that the load on the control unit 6 can be reduced.

[0033]

As described above, according to the compressed air dehumidifying device of the present invention, the control section controls the refrigerant compressing means in accordance with the temperature detected by the temperature detecting means to adjust the refrigerating capacity of the refrigerating cycle. By doing so, in summer (when the temperature is high outside), where it is not necessary to completely dehumidify the compressed air,
The power consumption of the refrigerant compression means can be sufficiently reduced. In this case, when the outdoor temperature is low, the control unit controls the refrigerant compression means to cool the inside of the heat exchanger to the dew point temperature, so that the compressed air is almost completely dehumidified,
It is possible to avoid dew condensation in the blower pipe. on the other hand,
In summer when the temperature is high outside, the inside of the heat exchanger is cooled to a temperature slightly higher than the dew point temperature.Therefore, when dehumidifying, the heat exchanger is discharged from the heat exchanger compared to the case where it is cooled to the dew point temperature. As a result of the temperature of the compressed air (compressed air after dehumidification) becoming high, dew condensation on the outer surface of the blower pipe can be avoided.

Further, according to the compressed air dehumidifying device of the present invention, the control unit controls the operating state of the inverter control type refrigerant compressor to adjust the pressure feeding capacity, so that the air compressed by the air compressor is controlled. Not only the refrigerant compression means can be adjusted according to the temperature (outdoor temperature), but also the pressure feeding ability can be finely adjusted according to the amount of compressed air fed by the air compressor. Therefore, the power consumption by the refrigerant compression means can be further reduced.

Further, according to the compressed air dehumidifying apparatus of the present invention, the control section individually controls the driving of each refrigerant compressor to adjust the pressure feeding capacity, thereby constituting the refrigerant compression means at a relatively low cost. Therefore, the manufacturing cost of the entire compressed air dehumidifier can be sufficiently reduced.

Further, according to the compressed air dehumidifying device of the present invention, the calculating unit calculates the temperature of the compressed air based on the room temperature detected by the temperature sensor and the temperature difference information stored in the storage unit. At the same time, the control unit controls the refrigerant compression unit according to the calculation result of the calculation unit, so that the temperature sensor is installed outdoors and the temperature of the outdoors is directly measured as compared with the temperature sensor. And the signal cable for the temperature sensor can be easily routed. In this case, the control unit controls the refrigerant compression unit according to the calculation result of the calculation unit to directly measure the outdoor temperature and control the refrigerant compression unit in the same manner as the control method of the refrigeration cycle. The capacity (compressing capacity of the compressor) can be adjusted appropriately.

Further, according to the compressed air dehumidifying device of the present invention, the control unit stores the temperature difference information obtained by correcting the temperature difference information stored in the memory unit as new temperature difference information in the memory unit. The refrigeration capacity of the refrigeration cycle can be appropriately adjusted based on the temperature difference information corrected according to the installation environment of the compressed air dehumidifier.

Further, according to the compressed air dehumidifying device of the present invention, the control section adjusts the pressure feeding ability of the refrigerant compressing means stepwise on the basis of the temperature detected by the temperature detecting means. As a result of facilitating the adjustment control as compared with the control method of adjusting in multiple stages or in multiple stages, it is not necessary to increase the processing capacity of the control unit, so that the manufacturing cost of the compressed air dehumidifier can be reduced accordingly. .

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a configuration of a dehumidifying device 1 according to an embodiment of the present invention.

FIG. 2 is a characteristic diagram showing the relationship between the temperature of the outdoor OD, the room temperature of the indoor ID1, and the temperature of the compressed air pressure-fed by the compressor C.

FIG. 3 is a configuration diagram showing an example of the positional relationship between the installation location of the dehumidifier 1 (building R1) and the supply destination of compressed air (supply target X of the building R1).

FIG. 4 is a configuration diagram showing a configuration of a conventional dehumidifying device 51.

[Explanation of symbols]

1 Dehumidifier 2 heat exchanger 2a inlet 2b outlet 2c, 2d drainage port 3 refrigeration cycle 4 inverter 5 memory 6 control unit 7 Operation part 9 Drain trap 12 Secondary cooling unit 21 evaporator 22 compressor 23 condenser 24 Receiver 25 Electronic expansion valve C compressor D1, D2 duct Dt temperature difference data Dp control data ID1, ID2 indoor t1, t2 temperature difference TS temperature sensor OD outdoors R1, R2 building S detection signal X supply target

Claims (6)

[Claims] 1. A compressed air dehumidifier for dehumidifying air compressed by an air compressor and introduced into a heat exchanger by an evaporator in a refrigeration cycle to dehumidify the moisture in the air. A variable-pressure-feed-quantity refrigerant compression unit capable of adjusting the pressure-feed amount of the vaporized refrigerant to the condenser of the refrigeration cycle, a temperature detection unit that detects the temperature of the air compressed by the air compressor, and the temperature detection unit. A compressed air dehumidifying device comprising: a control unit that controls the refrigerant compression unit based on the detected temperature to adjust the refrigerating capacity of the refrigeration cycle. 2. The refrigerant compression means comprises an inverter control type refrigerant compressor, and the control section adjusts the pumping capacity of the refrigerant compression means by controlling the operating state of the refrigerant compressor. The compressed air dehumidifier according to claim 1. 3. The refrigerant compression means comprises a plurality of refrigerant compressors, and the control section adjusts the pressure-feeding capacity of the refrigerant compression means by individually controlling the driving of each of the refrigerant compressors. The compressed air dehumidifying device according to claim 1. 4. A storage unit that stores temperature difference information about a temperature difference between a room temperature at a location where the compressed air dehumidifier is installed and a temperature of air compressed by the air compressor, and the temperature detection unit includes: A temperature sensor that detects the room temperature; and a calculator that calculates the temperature of the compressed air based on the room temperature detected by the temperature sensor and the temperature difference information stored in the storage unit. The compressed air dehumidifying device according to claim 1, wherein the control unit controls the refrigerant compression unit based on the temperature calculated by the calculation unit. 5. An operating unit configured to be able to input differential temperature correction information for correcting the differential temperature information stored in the storage unit, wherein the control unit is input via the operating unit. The differential temperature information stored in the storage unit is corrected based on the differential temperature correction information, and the corrected differential temperature information is stored in the storage unit as the new differential temperature information. Compressed air dehumidifier. 6. The compressed air dehumidification according to claim 1, wherein the control unit adjusts the pressure-feeding capability of the refrigerant compression unit in stages based on the temperature detected by the temperature detection unit. apparatus.