KR101856737B1 - Outdoor air imported type constant temperature and dehumidification air conditioning system provided with evaporation pressure compensation structure - Google Patents

Abstract

Provided is an outdoor air inducing type constant temperature and dehumidification air conditioning system provided with an evaporation pressure compensation structure capable of maintaining temperature and humidity in an internal space uniformly as a constant temperature and humidity system. The air conditioning system comprises: an outdoor air inducing passage for inducing outdoor air into the entire interior space; a discharge passage for discharging the air of the interior space to the outside; a blower mounted on the outdoor air inducing passage to blow outdoor air to the interior; a first dehumidifying and cooling heat exchanger for exchanging heat between the air induced into the interior through the outdoor air inducing passage and refrigerant to perform cooling and dehumidification; a second dehumidifying and cooling heat exchanger for exchanging heat between the air passing through the first dehumidifying and cooling heat exchanger and the refrigerant to perform cooling and dehumidification; and a reheating heat exchanger for exchanging heat between the air passing through the second dehumidifying and cooling heat exchanger and refrigerant gas of high temperature to perform heating and dehumidification. The first dehumidifying and cooling heat exchanger and the second dehumidifying and cooling heat exchanger have an evaporation pressure compensation refrigerant pipe, which is arranged inside a main refrigerant pipe through which refrigerant of low temperature flows, and is formed such that refrigerant of high temperature flows in a spiral form.

Description

[0001] The present invention relates to an outdoor air-introduced type constant temperature and dehumidification air conditioning system provided with evaporation pressure compensation structure,

More particularly, the present invention relates to an air conditioning system configured to introduce and discharge the entire outside air for constant temperature and humidity of the indoor space.

Generally, in a chemical plant, a pharmaceutical company, a semiconductor manufacturing factory, etc., it is necessary to maintain a constant temperature and humidity due to the characteristics of the manufacturing process. The constant temperature and humidity system used for this purpose is designed to keep the temperature and humidity inside the building constant. Such a constant temperature and humidity system should be able to maintain a suitable temperature and humidity constantly in accordance with the place and purpose of use. For this reason, the constant temperature and humidity system is operated throughout the year to maintain the constant temperature and humidity in the room.

Such a constant temperature and humidity system can control the room temperature through cooling or heating according to the room temperature. Among the devices constituting the constant temperature and humidity system, the cooler is driven to lower the room temperature when the room temperature is higher than the set temperature. Such a cooler controls the room temperature using a compressor, a condenser, an expansion valve, and an evaporator.

On the other hand, the constant temperature and humidity system uses a refrigeration cycle to lower the room temperature. As described above, when the air conditioner is driven to lower the room temperature, there is a problem that the indoor humidity is lowered.

To solve this problem, the constant temperature and humidity system can be humidified or dehumidified to keep the room humidity constant. For example, in a situation where dehumidification is necessary, the constant temperature and humidity system can operate the air conditioner to lower the humidity of the room. On the other hand, in a situation where humidification is required, the constant temperature and humidity system maintains the humidity of the room constantly by supplying water supplied from the outside to the room to maintain a constant humidity. However, there is a problem in that a considerable amount of heat energy is consumed in the process of making water vapor by heating the cold water and supplying steam to the room.

In addition, when a conventional thermo-hygrostat system is employed for constant temperature and humidity in an indoor space where harmful substances are generated, such as a chemical factory, a pharmaceutical company, and a semiconductor manufacturing factory, toxic substances accumulate in the room air.

Korean Patent No. 10-1214892 (December 17, 2012)

SUMMARY OF THE INVENTION It is an object of the present invention to solve the above-mentioned problems, and it is an object of the present invention to provide an evaporative pressure compensating device capable of efficiently maintaining the indoor space in constant temperature and humidity, Temperature dehumidifying air-conditioning system having the structure of the present invention.

In order to achieve the above object, an entire outside air introduction type constant temperature dehumidifying air conditioning system having an evaporation pressure compensation structure according to an embodiment of the present invention is a constant temperature and humidity system that constantly maintains the temperature and humidity of a certain indoor space,

An outside air introducing passage for introducing outside air into the entire interior space;

An exhaust path for exhausting the air in the indoor space to the outside; And

And a blower installed in the outside air introduction passage for blowing outside air into the room,

A first dehumidification cooling heat exchanger configured to cool and dehumidify the air introduced into the room through the outside air introduction path by heat exchange with the refrigerant;

A second dehumidification cooling heat exchanger configured to cool and dehumidify the air passing through the first dehumidification cooling heat exchanger by heat exchange with the refrigerant; And

And a heating reheat heat exchanger configured to heat and humidify the air passing through the second dehumidification cooling heat exchanger with the high temperature refrigerant gas,

The first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger are characterized by including an evaporation pressure compensating refrigerant tube arranged inside the main refrigerant tube through which the low temperature refrigerant flows and formed so that the high temperature refrigerant flows in a spiral form.

At least two compressors for sucking refrigerant gas of low temperature and low pressure and discharging refrigerant gas of high temperature and high pressure;

A four-way valve for switching the flow of the refrigerant discharged from the compressor;

A first three-way valve for proportionally distributing the high-temperature and high-pressure refrigerant gas supplied from the four-way valve to pass through the heating reheat heat exchanger or bypass the heating reheat heat exchanger;

A second heat exchanger provided in an end portion of a flow path through which the refrigerant which has been heat-exchanged with the air of the outside air introduction passage in the heating reheat heat exchanger and then liquefied and the refrigerant of high temperature and high pressure bypassing the heating reheat heat exchanger from the first three- Three-way valve;

A receiver tank connected to the second three-way valve through a flow path to temporarily receive the refrigerant;

A third external heat exchanger and a fourth external heat exchanger connected to the second three-way valve by a flow path to cool the refrigerant by heat exchange with an external air heat source and connected to the receiver tank and the flow path,

A drier and a sight glass sequentially disposed on a flow path of the refrigerant discharged from the receiver tank;

The refrigerant having passed through the sight glass is branched into two flow paths so that one flow path is connected to the first dehumidification cooling heat exchanger through the first electromagnetic valve and the first expansion valve and the remaining flow path is connected to the second solenoid valve, Valve, a third solenoid valve, and a third expansion valve to the second dehumidification cooling heat exchanger;

The refrigerant that is heat-exchanged with the air of the outside air introduction path in the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger is connected so as to join the four-way valve and the flow path connected to the suction port side of the compressor;

A third three-way valve disposed in a flow path branched on a flow path connecting the discharge port side of the compressor and the four-way valve;

One of the flow paths branched from the third three-way valve is connected to a flow path connecting the four-way valve and the first three-way valve, and the other is connected to a flow path connecting the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger Branched refrigerant pipe;

The refrigerant having passed through the evaporation pressure compensating refrigerant pipe of the first dehumidifying cooling heat exchanger is connected to flow into the fourth external heat exchanger through the fourth solenoid valve and the fourth expansion valve;

The refrigerant passing through the evaporation pressure compensating refrigerant pipe of the second dehumidification cooling heat exchanger is connected to flow into the third external heat exchanger through the fifth solenoid valve and the fifth expansion valve;

The refrigerant flowing into the fourth external heat exchanger through the fourth expansion valve and the refrigerant flowing into the third external heat exchanger through the fifth expansion valve are connected to flow to the four-way valve;

 A second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger;

And the sixth solenoid valve is connected to the third external heat exchanger among the auxiliary flow paths. A sixth expansion valve, a seventh solenoid valve, and a seventh expansion valve,

And an eighth solenoid valve, an eighth solenoid valve, a ninth solenoid valve, and a ninth solenoid valve are disposed in the passage of the auxiliary passage connected to the fourth external heat exchanger.

An outside air sensor for measuring the temperature and humidity of the air flowing into the outside air introduction path;

A first temperature controller for controlling the temperature of the air immediately after passing through the first dehumidification cooling heat exchanger among the air flowing through the outside air introduction path to proportionally control the capacity of the compressor;

A second temperature controller for controlling the temperature of the air immediately after passing through the second dehumidification cooling heat exchanger among the air flowing through the outside air introduction passage to proportionally control the capacity of the compressor;

A third temperature controller for controlling the opening and closing directions of the first three-way valve by measuring the temperature of air immediately after passing through the heating reheat heat exchanger among the air flowing through the outside air introduction path;

A temperature and humidity sensor for measuring the temperature and humidity of air immediately after passing through the heating reheat heat exchanger among the air flowing through the outside air introduction passage;

A first control module for controlling the opening and closing amount of the first expansion valve by measuring the temperature and the pressure of the refrigerant discharged from the first dehumidification cooling heat exchanger toward the inlet of the compressor;

A second control module for controlling the amount of opening and closing of the second expansion valve and the third expansion valve by measuring the temperature and pressure of the refrigerant discharged from the second dehumidification cooling heat exchanger toward the inlet of the compressor;

A fourth temperature controller for controlling the opening and closing directions of the second three-way valve by measuring the temperature of the refrigerant flowing into the second three-way valve;

A third control module for proportionally controlling the opening and closing amount of the third three-way valve based on the pressure of the refrigerant discharged from the first dehumidification cooling heat exchanger or the second dehumidification cooling heat exchanger toward the inlet of the compressor;

A fourth control module for controlling the amount of opening and closing of the sixth expansion valve and the seventh expansion valve by measuring the temperature and pressure of the refrigerant discharged from the third external heat exchanger toward the four-way valve; And

And a fifth control module for controlling the amount of opening and closing of the eighth expansion valve and the ninth expansion valve by measuring the temperature and pressure of the refrigerant discharged from the fourth external heat exchanger toward the four-

And an integrated controller for determining an integrated operation mode of the system based on the measured values of the ambient air sensor.

The entire outside air introduction type constant temperature dehumidifying air conditioning system equipped with the evaporation pressure compensation structure according to the present invention introduces the entire outside air for constant temperature and humidity in the indoor space to maintain the constant temperature and humidity and the introduced outside air is discharged to the outside, There is an effect that harmful substances are not accumulated. The entire outside air introduction type constant temperature dehumidifying air conditioning system provided with the evaporation pressure compensation structure according to the present invention is characterized in that the evaporation pressure of the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger is controlled by the high temperature high pressure refrigerant gas Exchanging the refrigerant with the refrigerant flowing through the main refrigerant pipe in the heat exchanger, thereby maintaining a stable constant temperature and humidity effect. Further, when the control modules for automatically controlling the main valves constituting the present system are provided as in the preferred embodiment of the present invention, there is an effect that the constant temperature and humidity effect can be maintained automatically and automatically during the year irrespective of seasonal changes.

1 is a schematic block diagram of an entire outside air introduction type constant temperature dehumidifying air conditioning system having an evaporation pressure compensation structure according to a preferred embodiment of the present invention.
FIG. 2 is a view schematically showing a structure of cooling fins of the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger included in FIG. 1. FIG.
FIG. 3 is a view for explaining a situation in which the constant temperature, dehumidified air conditioning system shown in FIG. 1 operates in summer.
FIG. 4 is a view showing the temperature and humidity change range of the air in the humidor diagram in the operation example shown in FIG. 3; FIG.
FIG. 5 is a view for explaining a situation where the constant temperature, dehumidified air conditioning system shown in FIG. 1 operates in the spring and autumn.
FIG. 6 is a view showing the temperature and humidity change range of the air in the operation diagram shown in FIG.
FIG. 7 is a diagram for explaining an operation example of the modified situation of FIG. 5; FIG.
8 is a view showing the temperature and humidity change range of the air in the operation diagram shown in Fig.
FIG. 9 is a view for explaining a situation in which the constant temperature, dehumidified air conditioning system shown in FIG. 1 operates in winter.
FIG. 10 is a view showing the temperature and humidity change range of the air in the humidifier diagram in the operation example shown in FIG. 9; FIG.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 is a schematic block diagram of an entire outside air introduction type constant temperature dehumidifying air conditioning system having an evaporation pressure compensation structure according to a preferred embodiment of the present invention. FIG. 2 is a view schematically showing a structure of cooling fins of the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger included in FIG. 1. FIG. FIG. 3 is a view for explaining a situation in which the constant temperature, dehumidified air conditioning system shown in FIG. 1 operates in summer. FIG. 4 is a view showing the temperature and humidity change range of the air in the humidor diagram in the operation example shown in FIG. 3; FIG. FIG. 5 is a view for explaining a situation where the constant temperature, dehumidified air conditioning system shown in FIG. 1 operates in the spring and autumn. FIG. 6 is a view showing the temperature and humidity change range of the air in the operation diagram shown in FIG. FIG. 7 is a diagram for explaining an operation example of the modified situation of FIG. 5; FIG. 8 is a view showing the temperature and humidity change range of the air in the operation diagram shown in Fig. FIG. 9 is a view for explaining a situation in which the constant temperature, dehumidified air conditioning system shown in FIG. 1 operates in winter. FIG. 10 is a view showing the temperature and humidity change range of the air in the humidifier diagram in the operation example shown in FIG. 9; FIG.

1 to 10, an entire outside air introduction type constant temperature dehumidifying air conditioning system 10 (hereinafter referred to as "air conditioning system") equipped with an evaporation pressure compensating structure according to the present invention includes a plurality of indoor air conditioning systems It is a constant temperature and humidity system that keeps temperature and humidity constant.

The air conditioning system 10 includes an outside air introduction passage 11, an exhaust passage 13, a blower 15, a compressor 20, a four-way valve 30, a first three- A second dehumidification cooling heat exchanger 50, a second three-way valve 70, a third external heat exchanger 93, and a second dehumidification cooling heat exchanger 50. The heat recovery heat exchanger 60, the first dehumidification cooling heat exchanger 40, the second dehumidification cooling heat exchanger 50, And a fourth external heat exchanger (94).

The outside air introducing passage 11 is a duct-type structure. One end of the outside air introducing passage 11 is thermally connected to the outside. The other end of the outside-air introducing passage 11 is connected to an indoor space 12 to be kept at constant temperature and humidity. The indoor space (12) includes an exhaust passage (13) for exhausting the air introduced through the outside air introduction path (11) to the outside. The outside air introduction path (11) is provided for introducing outside air into the entire interior space (12). It is preferable to provide an outside air sensor 200 for measuring the temperature and humidity of the air flowing into the outside air introducing passage 11.

The blower 15 may be installed at the end or the middle of the outside air introduction passage 11. It is preferable that the blower 15 is capable of proportionally controlling the amount of outdoor air introduced by the inverter motor. The blower 15 is a blowing device for blowing outside air into the indoor space 12.

The compressor (20) sucks the low-temperature low-pressure refrigerant gas and discharges the high-temperature high-pressure refrigerant gas. A oil separator 24 is provided in the oil passage on the discharge side of the compressor 20 to recover the oil contained in the refrigerant gas discharged from the compressor 20 to the compressor 20.

In the present invention, it is preferable that at least two compressors 20 are provided. For convenience of description, the two compressors 20 are defined as a first compressor 21 and a second compressor 22, respectively. The first compressor (21) and the second compressor (22) can regulate the output proportionally by a brushless inverter motor, respectively. The first compressor (21) and the second compressor (22) are preferably connected in parallel.

The four-way valve 30 is a device capable of switching the flow of the introduced refrigerant in one of three directions to flow. The four-way valve (30) is connected to the discharge port side of the compressor (20) by a flow path. The four-way valve (30) switches the flow of the refrigerant discharged from the compressor (20).

The first three-way valve (35) is a device for distributing the introduced refrigerant proportionally in two directions. The first three-way valve (35) is connected to the four-way valve (30) by a flow path. The first three-way valve 35 is connected to the heating reheat heat exchanger 60 so that the high-temperature high-pressure refrigerant gas supplied from the four-way valve 30 passes through the heating reheat heat exchanger 60 Distribution.

The heating reheat heat exchanger 60 heat-exchanges the air passing through the first dehumidification cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50 with a high-temperature refrigerant gas to perform heating and humidity . The temperature of the air immediately after passing through the heating reheat heat exchanger 60 in the air flowing through the outside air introducing path 11 is measured to determine the third temperature for proportionally controlling the amount of opening and closing of the first three- A regulator 213 is preferably provided. A temperature and humidity sensor 218 for measuring the temperature and humidity of the air immediately after passing through the heating reheat heat exchanger among the air flowing through the outside air introduction path 11 is preferably provided.

The high-temperature refrigerant gas flowing into the heating reheat heat exchanger (60) can be proportionally controlled by the first three-way valve (35). The amount of opening and closing of the first three-way valve 35 is controlled based on the temperature and humidity of the air just after passing through the heating reheat heat exchanger 60. The heating reheat heat exchanger (60) is configured to heat the air heated by the high-temperature and high-pressure refrigerant supplied from the first three-way valve (35) so that the temperature of the air can reach the target in an emergency An auxiliary heating coil 62 may be additionally provided.

The second three-way valve 70 is connected to the heating reheat heat exchanger 60 through the heat exchanging heat exchanger 60. The second three-way valve 70 exchanges heat with the air of the outside air introduction passage 11 in the heating reheat heat exchanger 60, Temperature and high-pressure refrigerant bypassing the unit (60) is installed at the end of the flow path through which the refrigerant flows. The amount of opening and closing of the second three-way valve 70 is controlled based on the temperature of the refrigerant measured by the fourth temperature regulator 214 installed at the inlet side of the second three-way valve 70. That is, the fourth temperature controller 214 measures the temperature of the refrigerant flowing into the second three-way valve 70 and controls the opening and closing directions of the second three-way valve 70.

And a receiver tank (80) connected to the second three-way valve (70) by a flow path to temporarily receive the refrigerant. The receiver tank 80 temporarily receives the refrigerant introduced from the second three-way valve 70 and discharges the refrigerant to the dryer 85 to be described later at a constant pressure.

Meanwhile, the second three-way valve (70) is connected to the third external heat exchanger (93) and the fourth external heat exchanger (94) by a flow path. The third external heat exchanger 93 and the fourth external heat exchanger 94 may have the same structure. The third external heat exchanger (93) and the fourth external heat exchanger (94) are arranged in parallel. The third external heat exchanger (93) and the fourth external heat exchanger (94) exchange heat between the external air heat source and the refrigerant. The refrigerant introduced from the second three-way valve (70) in the third external heat exchanger (93) and the fourth external heat exchanger (94) is cooled by heat exchange with an external air heat source. The third external heat exchanger (93) and the fourth external heat exchanger (94) are connected to the receiver tank (80) by a flow path. Therefore, all of the refrigerant having passed through the first three-way valve 35 is temporarily stored in the receiver tank 80. The third external heat exchanger 93 is provided with a separate refrigerant passage for allowing the refrigerant discharged from the evaporation pressure compensating refrigerant pipe 47 of the second dehumidification cooling heat exchanger 50 to be heat-exchanged with the external air heat source Respectively. The fourth external heat exchanger 94 is provided with a separate refrigerant passage for allowing the refrigerant discharged from the evaporation pressure compensating refrigerant pipe 47 of the first dehumidifying cooling heat exchanger 40 to be heat-exchanged with the external air heat source Respectively.

The dryer 85 and the sight glass 86 are sequentially disposed on the flow path through which the refrigerant discharged from the receiver tank 80 flows. In the dryer 85, the moisture of the refrigerant discharged from the receiver tank 80 is removed. The sight glass 86 is a device provided so that the refrigerant can flow normally or can be observed from the outside.

The refrigerant that has passed through the site glass 86 flows into the first dehumidification cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50 through the flow path.

The refrigerant having passed through the site glass 86 is branched into two flow paths. One of the two flow paths is connected to the first dehumidification cooling heat exchanger (40) through the first electromagnetic valve (100) and the first expansion valve (101). And the remaining one of the two flow paths is connected to the second dehumidification cooling heat exchanger (50). In the first expansion valve (101), the refrigerant undergoes thermal expansion to become a low-temperature low-pressure humidified vapor. A first control module 311 for controlling the opening and closing amount of the first expansion valve 101 by measuring the temperature and pressure of the refrigerant discharged from the first dehumidification cooling heat exchanger 40 toward the inlet of the compressor 20, .

The flow path connecting the site glass 86 and the second dehumidification cooling heat exchanger 50 is provided with a second electromagnetic valve 103, a second expansion valve 104, A third solenoid valve 106, and a third expansion valve 107 are disposed. The refrigerant is controlled to flow into the first dehumidification cooling heat exchanger (40) by opening and closing the first electromagnetic valve (100). Also, it is controlled that refrigerant flows into the second dehumidification cooling heat exchanger (50) in accordance with the opening and closing of the second electromagnetic valve (103) and the third electromagnetic valve (106). In the second expansion valve (104) and the third expansion valve (107), the refrigerant undergoes a thermal expansion to become a low-temperature low-pressure humidified vapor. The amount of opening and closing of the second expansion valve 104 and the third expansion valve 107 is controlled by measuring the temperature and pressure of the refrigerant discharged from the second dehumidification cooling heat exchanger 50 toward the inlet of the compressor 20 A second control module 312 is provided.

The first dehumidifying cooling heat exchanger (40) is a device for cooling and dehumidifying the air introduced into the room through the outside air introducing passage (11) by heat exchange with the refrigerant. A first temperature regulator (not shown) for measuring the temperature of air immediately after passing through the first dehumidification cooling heat exchanger (40) among the air flowing through the outside air introduction path (11) and controlling the capacity of the compressor 211 may be provided.

The second dehumidification cooling heat exchanger (50) is a device for cooling and dehumidifying the air passing through the first dehumidification cooling heat exchanger (40) by heat exchange with the refrigerant. A second temperature regulator (not shown) for measuring the temperature of the air immediately after passing through the second dehumidification cooling heat exchanger (50) among the air flowing through the outside air introduction path (11) and controlling the capacity of the compressor 212 are preferably provided.

The refrigerant cooled by heat exchange with the air of the outside air introduction path 11 in the first dehumidification cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50 is supplied to the four way valve 30 and the compressor 20 To the intake port side of the engine. A gas-liquid separator (26) is provided in the inlet-side passage of the compressor (20) to prevent liquid refrigerant from flowing into the compressor (20).

As shown in FIG. 2, the first dehumidification cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50 are disposed inside the main refrigerant pipe 45 through which the low temperature refrigerant flows, And an evaporation pressure compensating refrigerant tube (47) formed to flow therethrough. When the evaporation pressure of the refrigerant flowing through the main refrigerant pipe (45) of the first dehumidification cooling heat exchanger (40) or the second dehumidification cooling heat exchanger (50) is not sufficient, the evaporation pressure compensating refrigerant pipe (47) Temperature and high-pressure refrigerant gas discharged to the compressor (20) in a proportional manner so that the evaporation pressure of the refrigerant flowing through the main refrigerant pipe (45) is ideally maintained.

A third three-way valve (75) is disposed in a flow path branched on a flow path connecting the discharge port side of the compressor (20) and the four-way valve (30).

One of the flow paths branched from the third three-way valve (75) is connected to a flow path connecting the four-way valve (30) and the first three-way valve (35). The remaining one of the flow channels branched from the third three-way valve (75) branches to the evaporation pressure compensating refrigerant pipe (47) provided in the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) Respectively. Closing amount of the third three-way valve 75 based on the pressure of the refrigerant discharged from the first dehumidification cooling heat exchanger 40 or the second dehumidification cooling heat exchanger 50 toward the inlet of the compressor 20 It is preferable that the third control module 313 is provided for proportionally controlling. A tenth solenoid valve (160) is installed in the flow path connecting the third three-way valve (75) to the evaporation pressure compensating refrigerant pipe (47) of the first dehumidification cooling heat exchanger (40). An eleventh solenoid valve 170 is installed in the flow path connecting the third three-way valve 75 and the evaporation pressure compensating refrigerant pipe 47 of the second dehumidification cooling heat exchanger 50.

The refrigerant having passed through the evaporation pressure compensating refrigerant pipe 47 of the first dehumidification cooling heat exchanger 40 passes through the fourth electromagnetic valve 118 and the fourth expansion valve 120 and flows into the fourth external heat exchanger 94 As shown in FIG.

The refrigerant passing through the evaporation pressure compensating refrigerant pipe 47 of the second dehumidification cooling heat exchanger 50 passes through the fifth solenoid valve 128 and the fifth expansion valve 130 and flows through the third external heat exchanger 93 As shown in FIG.

The refrigerant flowing into the fourth external heat exchanger 94 through the fourth expansion valve 120 and the refrigerant flowing into the third external heat exchanger 93 through the fifth expansion valve 130 are combined Way valve (30).

And a second dehumidifying cooling heat exchanger (50) that is connected to the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) through the site glass (86) And an auxiliary flow path P1 flowing into the external heat exchanger 94 are provided.

The sixth solenoid valve 140, the sixth expansion valve 142, the seventh solenoid valve 144, and the seventh expansion valve 146 (not shown) are connected to the third outer heat exchanger 93, Are arranged in parallel to each other. The amount of opening and closing of the sixth expansion valve 142 and the seventh expansion valve 146 is controlled by measuring the temperature and the pressure of the refrigerant discharged from the third external heat exchanger 93 toward the four- It is preferable that a fourth control module 314 is provided. A fifth temperature regulator 215 for proportionally controlling the blowing amount of the third external heat exchanger 93 based on the pressure of the refrigerant discharged from the third external heat exchanger 93 toward the four-way valve 30 . The fifth temperature regulator 215 proportionally controls the blowing fan of the third external heat exchanger 93 by a brushless inverter motor.

The eighth electromagnetic valve 147, the eighth expansion valve 148, the ninth solenoid valve 150, and the ninth expansion valve 152 (not shown) are connected to the flow path of the auxiliary flow path P1 to the fourth external heat exchanger 94, Are arranged in parallel to each other. And controls the amount of opening and closing of the eighth expansion valve (148) and the ninth expansion valve (152) by measuring the temperature and pressure of the refrigerant discharged from the fourth external heat exchanger (94) toward the four- It is preferable that a fifth control module 315 is provided. A sixth temperature regulator 216 for proportionally controlling the blowing amount of the fourth external heat exchanger 94 based on the pressure of the refrigerant discharged from the fourth external heat exchanger 94 toward the four-way valve 30 . The sixth temperature regulator 216 proportionally controls the blowing fan of the fourth external heat exchanger 94 by a brushless inverter motor.

And an integrated controller (not shown) for determining an integrated operation mode of the system based on the measured values of the ambient air sensor 200. [ The integrated controller is a central control device that integrally controls the plurality of sensors and control modules described above.

Components such as valves and flow paths not specifically described in the drawings will be readily understood by those skilled in the art to which the present invention pertains, and will not hinder the understanding of the present invention.

Hereinafter, the operation and effect of the present invention will be described in detail with respect to the flow of refrigerant and the flow of air, by dividing the operation and effect of the present invention into several cases according to the temperature and humidity environment of the outside air.

First, a case where the temperature of the outside air is 30 DEG C or more as in the summer is defined as the first operation mode. The first operating mode is, for example, when the temperature of the outside air is 33 캜 and the humidity is 75%, and operates to maintain the air in the room at a relative humidity of 20 캜 to 24 캜 at 50%. In this case, the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) also operate at 100% efficiency.

Referring to FIGS. 3 and 4, the blower 15 operates to blow outside air into the indoor space. The outside air passes through the outside dehumidifying cooling heat exchanger (40), the second dehumidification cooling heat exchanger (50), and the heating reheat heat exchanger (60) sequentially along the outside air introduction path (11) (12). In this process, we explain in detail how the air and refrigerant exchange heat. The first compressor (21) and the second compressor (22) are operated proportionally according to the required capacity to discharge refrigerant gas of high temperature and high pressure toward the four-way valve (30). The high-temperature and high-pressure refrigerant gas flows into the four-way valve 30 through the point a, flows in the direction a -> c, and flows in the direction a -> b from the first three-way valve 35. The refrigerant flowing from the first three-way valve 35 into the heating reheat heat exchanger 60 is cooled and dehumidified by the first dehumidification cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50, Heat and humidify the lowered air to reach the target temperature and humidity. In this process, the first three-way valve 35 proportionally controls the flow of the refrigerant in the directions a -> b and a-> c according to the temperature set in the third temperature controller 213. The refrigerant passing through the first three-way valve (35) and passing through the heating reheat heat exchanger (60) is liquefied and reaches the point (b). The refrigerant bypassed from the heating reheat heat exchanger is merged at the point of the high temperature and high pressure gas state. After the temperature of the indoor space is adjusted by the above process, the refrigerant joins the refrigerant at point b and flows into the second three-way valve 70. The second three-way valve 70 flows in a direction a -> b or a -> c depending on the temperature value set in the fourth temperature regulator 214. When the refrigerant is equal to or higher than the set value of the fourth temperature regulator 214, it flows in the direction a -> b. When the refrigerant is lower than the set value of the fourth temperature regulator 214, it flows in the direction a -> c. The refrigerant that has passed through the second three-way valve 70 in the direction a -> b flows into the third external heat exchanger 93 and the fourth external heat exchanger 94. In the third external heat exchanger (93) and the fourth external heat exchanger (94), the external air heat source and the refrigerant undergo heat exchange. As a result, the refrigerant in the gaseous state at high temperature and high pressure is phase-changed into the liquid state, merges at the point of the liquid, and flows into the receiver tank 80 through the point. On the other hand, the refrigerant flowing in the direction of a - > c from the second three-way valve 70 passes through the third outdoor heat exchanger 93 and the fourth outdoor heat exchanger 94, (80). The liquid refrigerant flowing into the receiver tank 80 passes through the dryer 85 and the sight glass 86 while passing through the point ⓒ and flows into the boiling point. The refrigerant passing through the first and second expansion valves 101 and 102 flows into the first dehumidification cooling heat exchanger 40 after being phase-changed into the low-temperature and low-pressure humidified steam by being thermally expanded through the first electromagnetic valve 100 and the first expansion valve 101, Respectively. Exchanges heat with the air introduced from the outside through the outside air introducing path 11 in the first dehumidifying cooling heat exchanger 40 to primarily adjust the temperature and humidity of the air to a value set in the first temperature controller 211 . At this time, since the capacity of the first compressor (21) can be adjusted by the variable control according to the temperature value set in the first temperature controller (211), the temperature and the dehumidifying amount of the constant value can be adjusted. At this time, the liquid refrigerant introduced into the boiling point passes through the second solenoid valve 103 and the second expansion valve 104, passes through the third solenoid valve 106 and the third expansion valve 107, And then flows into the second dehumidification cooling heat exchanger (50). The refrigerant in the second dehumidification cooling heat exchanger (50) is heat-exchanged with air primarily dehumidified and cooled while passing through the first dehumidification cooling heat exchanger (40), and the air is set in the second temperature controller It can be controlled by temperature and humidity. At this time, the second compressor (22) can adjust the capacity by variable control according to the temperature value set in the second temperature controller (212), so that it is possible to adjust the temperature and the humidity of a certain value. At this time, the refrigerant having performed the primary dehumidification and cooling function through the first dehumidification cooling heat exchanger (40) is joined to the flow path connected to the suction port of the compressor (20) at the point of e. Further, the refrigerant having performed the secondary dehumidification and cooling function through the second dehumidification cooling heat exchanger (50) is joined to the flow path connected to the inlet of the compressor (20) at point d. Further, the refrigerant passing through the point E or the point D is passed through the gas-liquid separator 26 to separate the liquid refrigerant, and the gaseous refrigerant flows into the compressor 20 to complete the refrigeration cycle. In this process, the primary and secondary dehumidified and cooled air in the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) flows into the heating reheat heat exchanger (60). In the heating reheat heat exchanger (60), the high temperature and high pressure refrigerant gas passing through the first three-way valve (35) in the a-> b direction is heat-exchanged with the air according to the temperature set in the third temperature regulator (213) Is finally heated and humidified and then supplied to the indoor space (12). Through the above process, the outside air is cooled and humidified at a temperature of 33 ° C and a humidity of 75% in a state of 20 ° C to 24 ° C and a humidity of 50%, and is supplied to the interior space 12.

Now, a case where the temperature of the outside air is 20 占 폚 or more and less than 30 占 폚 as in spring and autumn is defined and explained as the second operation mode. The second operating mode is, for example, a case where the temperature of the outside air is 24 캜 and the humidity is 95%, and the indoor air is operated to maintain the air at 50% relative humidity of 20 캜 to 24 캜. In this case, the first dehumidification cooling heat exchanger (40) operates at 100% efficiency, and the second dehumidification cooling heat exchanger (50) operates at 50% efficiency.

Referring to FIGS. 5 and 6, the blower 15 operates to blow outside air into the indoor space. The outside air passes through the outside dehumidifying cooling heat exchanger (40), the second dehumidification cooling heat exchanger (50), and the heating reheat heat exchanger (60) sequentially along the outside air introduction path (11) (12). In this process, we explain in detail how the air and refrigerant exchange heat. The first compressor (21) and the second compressor (22) are operated proportionally according to the required capacity to discharge refrigerant gas of high temperature and high pressure toward the four-way valve (30). The high-temperature, high-pressure refrigerant gas flows into the four-way valve 30 through the point a, flows in the direction a -> c, and flows in the direction a -> b from the first three-way valve 35. The refrigerant flowing from the first three-way valve 35 into the heating reheat heat exchanger 60 is cooled and dehumidified by the first dehumidification cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50, Heat and humidify the lowered air to reach the target temperature and humidity. In this process, the first three-way valve 35 proportionally controls the flow of the refrigerant in the directions a -> b and a-> c according to the temperature set in the third temperature controller 213. The refrigerant passing through the first three-way valve (35) and passing through the heating reheat heat exchanger (60) is liquefied and reaches the point (b). The refrigerant bypassed from the heating reheat heat exchanger is merged at the point of the high temperature and high pressure gas state. After the temperature of the indoor space is adjusted by the above process, the refrigerant joins the refrigerant at point b and flows into the second three-way valve 70. The second three-way valve 70 flows in a direction a -> b or a -> c depending on the temperature value set in the fourth temperature regulator 214. When the refrigerant is equal to or higher than the set value of the fourth temperature regulator 214, it flows in the direction a -> b. When the refrigerant is lower than the set value of the fourth temperature regulator 214, it flows in the direction a -> c. The refrigerant that has passed through the second three-way valve 70 in the direction a -> b flows into the third external heat exchanger 93 and the fourth external heat exchanger 94. In the third external heat exchanger (93) and the fourth external heat exchanger (94), the external air heat source and the refrigerant undergo heat exchange. As a result, the refrigerant is phase-changed into the liquid state, merges at the boiling point, and flows into the receiver tank 80 through the boiling point. On the other hand, the refrigerant flowing in the direction of a - > c from the second three-way valve 70 passes through the third outdoor heat exchanger 93 and the fourth outdoor heat exchanger 94, (80). The liquid refrigerant flowing into the receiver tank 80 passes through the dryer 85 and the sight glass 86 while passing through the point ⓒ and flows into the boiling point. The refrigerant passing through the first and second expansion valves 101 and 102 flows into the first dehumidification cooling heat exchanger 40 after being phase-changed into the low-temperature and low-pressure humidified steam by being thermally expanded through the first electromagnetic valve 100 and the first expansion valve 101, Respectively. Exchanges heat with the air introduced from the outside through the outside air introducing path 11 in the first dehumidifying cooling heat exchanger 40 to primarily adjust the temperature and humidity of the air to a value set in the first temperature controller 211 . At this time, since the capacity of the first compressor (21) can be adjusted by the variable control according to the temperature value set in the first temperature controller (211), the temperature and the dehumidifying amount of the constant value can be adjusted. When the refrigerant pressure of the low pressure refrigerant at the outlet of the main refrigerant pipe (45) of the first dehumidifying cooling heat exchanger (40) drops below the set value of the third control module, the third control module (313) Pressure refrigerant gas flowing into the third three-way valve 75 through the point a from the first dehumidification cooling heat exchanger 40 through the tenth solenoid valve 160 To the evaporation pressure compensating refrigerant pipe 47 of the evaporator. The heat exchange between the refrigerant flowing through the main refrigerant pipe 45 of the first dehumidifying cooling heat exchanger 40 and the refrigerant flowing through the evaporation pressure compensating refrigerant pipe 47 occurs and the main refrigerant pipe of the first dehumidification cooling heat exchanger 40 45), the problem that the dehumidification cooling capacity of the first dehumidification cooling heat exchanger (40) is lowered is solved by preventing the evaporation pressure of the refrigerant at the outlet side from being lowered. Also, heat exchange is performed between the main refrigerant pipe (45) of the first dehumidification cooling heat exchanger (40) and the evaporation pressure compensating refrigerant pipe (47), so that the outside of the heat exchanging pin of the first dehumidifying cooling heat exchanger There is an effect of preventing occurrence. Accordingly, the pressure of the refrigerant discharged from the main refrigerant pipe (45) of the first dehumidification cooling heat exchanger (40) can be kept constant, so that the constant temperature dehumidifying air conditioning system can be stably operated.

The refrigerant gas of high temperature and high pressure which has been subjected to evaporation pressure compensation in the first dehumidification cooling heat exchanger (40) flows into the fourth expansion valve (120) through the fourth electromagnetic valve (118) And flows into the fourth external heat exchanger (94). In the fourth external heat exchanger (94), the external air heat source and the refrigerant undergo heat exchange to convert the refrigerant into the superheated gas of low temperature and low pressure. The refrigerant discharged from the fourth external heat exchanger 94 passes through the dew point and passes through the four-way valve 30 in the direction b -> d and flows through the dew point e and the gas-liquid separator 26, And the gaseous refrigerant flows into the suction port of the compressor 20, thereby completing the first constant temperature and humidity cycle.

At this time, the liquid refrigerant introduced into the boiling point passes through the second solenoid valve 103 and the second expansion valve 104, is phase-changed into low-temperature low-pressure humidified vapor, and then flows into the second dehumidification cooling heat exchanger 50, Lt; / RTI > At this time, the third solenoid valve 106 is kept closed and the refrigerant can not pass through the third expansion valve 107. Therefore, the second dehumidification cooling heat exchanger (50) is operated at an efficiency of 50%. The refrigerant in the second dehumidification cooling heat exchanger (50) is heat-exchanged with air primarily dehumidified and cooled while passing through the first dehumidification cooling heat exchanger (40), and the air is set in the second temperature controller It can be controlled by temperature and humidity. At this time, the second compressor (22) can adjust the capacity by variable control according to the temperature value set in the second temperature controller (212), so that it is possible to adjust the temperature and the humidity of a certain value. At this time, if the second compressor (22) operates 100% in accordance with the insufficient heating capacity of the heating reheat heat exchanger (60), the second dehumidification cooling heat exchanger (50) (93) can also be operated at 50% and the overall capacity balance can be maintained. That is, a part of the liquid refrigerant discharged from the receiver tank 80 flows at the point of " c " and flows along the auxiliary flow path " P1 ", passes through the point of the sixth solenoid valve 140 and the sixth expansion valve 142 And flows into the third external heat exchanger 93 sequentially through the point and the point after the phase transformation into the low-temperature low-pressure low-temperature and low-pressure vapor state. In the third external heat exchanger (93), the refrigerant is heat-exchanged with the external air heat source to become superheated steam of low temperature and low pressure, passes through the point, passes through the four-way valve (30) in the direction b -> d, Liquid refrigerant in the gas-liquid separator 26, and the gaseous refrigerant flows into the suction port of the compressor 20, so that the evaporation source of heat due to the 100% operation of the second compressor 22 can be solved.

The refrigerant low-pressure evaporation pressure on the outlet side of the main refrigerant pipe (45) of the second dehumidification cooling heat exchanger (50) is changed to the third evaporation temperature of the third dehumidification cooling heat exchanger When the temperature of the refrigerant is lower than the set value of the control module, the third control module 313 passes the high-temperature and high-pressure refrigerant gas flowing into the third three-way valve 75 through the point a, And flows to the evaporation pressure compensating refrigerant pipe (47) of the second dehumidification cooling heat exchanger (50) through the solenoid valve (170). The heat exchange between the refrigerant flowing through the main refrigerant pipe 45 of the second dehumidification cooling heat exchanger 50 and the refrigerant flowing through the evaporation pressure compensating refrigerant pipe 47 occurs and the main refrigerant pipe of the second dehumidification cooling heat exchanger 50 45, the evaporation pressure of the refrigerant at the outlet side is not lowered, thereby solving the problem that the dehumidification cooling capacity of the second dehumidification cooling heat exchanger (50) is lowered. Further, heat exchange is performed between the main refrigerant pipe (45) of the second dehumidification cooling heat exchanger (50) and the evaporation pressure compensating refrigerant pipe (47), so that the outside of the heat exchanging pin of the second dehumidifying cooling heat exchanger There is an effect of preventing the occurrence of the problem. Therefore, the pressure of the refrigerant discharged from the main refrigerant pipe (45) of the second dehumidification cooling heat exchanger (50) can be kept constant despite the environment change, so that the constant temperature and humidity dehumidifying air conditioning system can be stably operated.

The high-temperature and high-pressure refrigerant gas after the evaporation pressure compensation in the second dehumidification cooling heat exchanger (50) flows into the fifth expansion valve (130) through the fifth solenoid valve (128) And flows into the third external heat exchanger (93). In the third external heat exchanger (93), the external air heat source and the refrigerant undergo heat exchange to convert the refrigerant into the superheated gas of the low temperature and the low pressure. The refrigerant discharged from the third external heat exchanger 93 passes through the dew point and passes through the four-way valve 30 in the direction b -> d and flows through the dew point e and the gas-liquid separator 26 to the liquid refrigerant And the gaseous refrigerant flows into the suction port of the compressor 20, thereby completing the second constant temperature and humidity cycle.

In this process, the refrigerant having performed the primary dehumidification and cooling function through the first dehumidification cooling heat exchanger (40) is joined to the flow path connected to the suction port of the compressor (20) at the point of e. Further, the refrigerant having performed the secondary dehumidification and cooling function through the second dehumidification cooling heat exchanger (50) is joined to the flow path connected to the inlet of the compressor (20) at point d. Further, the refrigerant passing through the point E or the point D is passed through the gas-liquid separator 26 to separate the liquid refrigerant, and the gaseous refrigerant flows into the compressor 20 to complete the refrigeration cycle. In this process, the primary and secondary dehumidified and cooled air in the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) flows into the heating reheat heat exchanger (60). In the heating reheat heat exchanger (60), the high temperature and high pressure refrigerant gas passing through the first three-way valve (35) in the a-> b direction is heat-exchanged with the air according to the temperature set in the third temperature regulator (213) Is finally heated and humidified and then supplied to the indoor space (12). After the above process, the outside air is cooled and humidified at a temperature of 24 ° C and a humidity of 95% at a temperature of 20 ° C to 24 ° C and a humidity of 50%, and is supplied to the indoor space 12.

Now, the case where the temperature of the outside air is kept below 20 占 폚 in the spring / autumn season and early winter is defined and explained as the third operation mode. The third operating mode is, for example, an operation in which the air in the indoor space is maintained at 50% relative humidity of 20 ° C to 24 ° C when the temperature of the outside air is 16 ° C and the humidity is 95%. In this case, the first dehumidification cooling heat exchanger (40) does not operate, and the second dehumidification cooling heat exchanger (50) operates at 50% efficiency.

Referring to FIGS. 7 and 8, the blower 15 operates to blow outside air into the indoor space. The outside air passes through the outside dehumidifying cooling heat exchanger (40), the second dehumidification cooling heat exchanger (50), and the heating reheat heat exchanger (60) sequentially along the outside air introduction path (11) (12). In this process, we explain in detail how the air and refrigerant exchange heat. The first compressor (21) and the second compressor (22) are operated proportionally according to the required capacity to discharge refrigerant gas of high temperature and high pressure toward the four-way valve (30). For example, the first compressor 21 is operated for the purpose of dehumidifying cooling of the second dehumidification cooling heat exchanger 50 and is also used as a heat source of the heating reheat heat exchanger 60. On the other hand, when the heating capacity of the heating reheat heat exchanger (60) is insufficient, the second compressor (22) forms a high temperature and high pressure refrigerant gas by variable control operation and discharges it. The high-temperature, high-pressure refrigerant gas discharged from the first compressor (21) and the second compressor (22) flows into the four-way valve (30) Flows in the direction a - > b from (35). The refrigerant flowing from the first three-way valve 35 to the heating reheat heat exchanger 60 passes through the first dehumidification cooling heat exchanger 40 and is cooled and dehumidified by the second dehumidification cooling heat exchanger 50 Heat and humidify the lowered air to reach the target temperature and humidity. In this process, the first three-way valve 35 proportionally controls the flow of the refrigerant in the directions a -> b and a-> c according to the temperature set in the third temperature controller 213. The refrigerant passing through the first three-way valve (35) and passing through the heating reheat heat exchanger (60) is liquefied and reaches the point (b). The refrigerant bypassed by the heating reheat heat exchanger is merged at the point of b in the gaseous state. After the temperature of the indoor space is adjusted by the above process, the refrigerant joins the refrigerant at point b and flows into the second three-way valve 70. The second three-way valve 70 flows in a direction a -> b or a -> c depending on the temperature value set in the fourth temperature regulator 214. When the refrigerant is equal to or higher than the set value of the fourth temperature regulator 214, it flows in the direction a -> b. When the refrigerant is lower than the set value of the fourth temperature regulator 214, it flows in the direction a -> c. The refrigerant that has passed through the second three-way valve 70 in the direction a -> b flows into the third external heat exchanger 93 and the fourth external heat exchanger 94. In the third external heat exchanger (93) and the fourth external heat exchanger (94), the external air heat source and the refrigerant undergo heat exchange. In this process, the third external heat exchanger (93) is controlled by the fifth temperature regulator (215) to be blown by the blower fan of the external air blown by the inverter motor, and the fourth external heat exchanger (94) 6 The amount of blowing of the outside air is controlled by the temperature controller 216 to the blowing fan operated by the inverter motor. As a result, the refrigerant is phase-changed into the liquid state, merges at the boiling point, and flows into the receiver tank 80 through the boiling point. On the other hand, the refrigerant flowing in the direction of a - > c from the second three-way valve 70 passes through the third outdoor heat exchanger 93 and the fourth outdoor heat exchanger 94, (80).

The liquid refrigerant flowing into the receiver tank 80 flows through the dryer 85 and the sight glass 86, passing through the point ⓒ, and flowing into the dryer. In this state, the first solenoid valve 100 remains closed. Therefore, the refrigerant does not flow into the first dehumidification cooling heat exchanger (40). As a result, in the first dehumidification cooling heat exchanger (40), heat exchange between the outside air and the refrigerant does not occur. As a result, the temperature of the outside air passing through the first dehumidifying cooling heat exchanger (40) is maintained at 16 DEG C and the humidity is 95%. The refrigerant passing through the point passes through the second electromagnetic valve (103) and the second expansion valve (104), is thermally expanded, is phase-changed into low-temperature low-pressure low-pressure humidified vapor, and then flows into the second dehumidification cooling heat exchanger do. At this time, the third solenoid valve 106 is kept closed and the refrigerant can not pass through the third expansion valve 107. Therefore, the second dehumidification cooling heat exchanger (50) is operated at an efficiency of 50%. In the second dehumidification cooling heat exchanger (50) The refrigerant is heat-exchanged with the air passing through the first dehumidification cooling heat exchanger (40), and the air can be adjusted to the temperature and humidity set in the second temperature controller (212). The refrigerant low-pressure evaporation pressure on the outlet side of the main refrigerant pipe (45) of the second dehumidification cooling heat exchanger (50) is changed to the third evaporation temperature of the third dehumidification cooling heat exchanger When the temperature of the refrigerant is lower than the set value of the control module, the third control module 313 passes the high-temperature and high-pressure refrigerant gas flowing into the third three-way valve 75 through the point a, And flows to the evaporation pressure compensating refrigerant pipe (47) of the second dehumidification cooling heat exchanger (50) through the solenoid valve (170). The heat exchange between the refrigerant flowing through the main refrigerant pipe 45 of the second dehumidification cooling heat exchanger 50 and the refrigerant flowing through the evaporation pressure compensating refrigerant pipe 47 occurs and the main refrigerant pipe of the second dehumidification cooling heat exchanger 50 45, the evaporation pressure of the refrigerant at the outlet side is not lowered, thereby solving the problem that the dehumidification cooling capacity of the second dehumidification cooling heat exchanger (50) is lowered. Further, heat exchange is performed between the main refrigerant pipe (45) of the second dehumidification cooling heat exchanger (50) and the evaporation pressure compensating refrigerant pipe (47), so that the outside of the heat exchanging pin of the second dehumidifying cooling heat exchanger There is an effect of preventing the occurrence of the problem. Therefore, the pressure of the refrigerant discharged from the main refrigerant pipe (45) of the second dehumidification cooling heat exchanger (50) can be kept constant despite the environment change, so that the constant temperature and humidity dehumidifying air conditioning system can be stably operated.

The high-temperature and high-pressure refrigerant gas after the evaporation pressure compensation in the second dehumidification cooling heat exchanger (50) flows into the fifth expansion valve (130) through the fifth solenoid valve (128) And flows into the third external heat exchanger (93). In the third external heat exchanger (93), the external air heat source and the refrigerant undergo heat exchange to convert the refrigerant into the superheated gas of the low temperature and the low pressure. The refrigerant discharged from the third external heat exchanger 93 passes through the dew point and passes through the four-way valve 30 in the direction b -> d and flows through the dew point e and the gas-liquid separator 26 to the liquid refrigerant And the gaseous refrigerant flows into the suction port of the compressor 20, thereby completing the second constant temperature and humidity cycle.

In this process, the refrigerant having performed the dehumidification and cooling functions through the second dehumidification cooling heat exchanger (50) is joined to the flow path connected to the suction port of the compressor (20) at point d. In addition, the refrigerant passing through the point (d) passes through the gas-liquid separator (26) to separate the liquid refrigerant, and the gaseous refrigerant flows into the compressor (20) to complete the refrigeration cycle. At this time, it takes about 50% of the dehumidifying cooling low temperature heat source in the second dehumidification cooling heat exchanger 50 and the evaporation heat source cycle of about 50% is discharged from the receiver tank 80, Respectively. Half of the refrigerant passing through the boiling point passes through the sixth solenoid valve 140 and the sixth expansion valve 142 to undergo a monotonous expansion and is phase-changed into a low-temperature low-pressure humidified vapor, And then flows into the heat exchanger (93). At this time, since the seventh solenoid valve 144 is kept closed, the refrigerant does not flow into the seventh expansion valve 146. Further, the remainder of the refrigerant that has passed through the dew point passes through the dew point and is subjected to the thermal expansion while passing through the eighth solenoid valve 147, the eighth expansion valve, the ninth solenoid valve 150 and the ninth expansion valve 152 And then flows into the fourth external heat exchanger 94 through the dew point after the phase change to the low-temperature low-pressure wetted vapor state. The refrigerant is heat-exchanged with the external air heat source at the third external heat exchanger 93 and the fourth external heat exchanger 94 to be superheated steam of low temperature and low pressure and merges at a point to form the four- Liquid separator 26, and the gaseous refrigerant flows into the suction port side of the compressor 20, thereby completing the refrigeration cycle.

In this process, the dehumidified and cooled air in the second dehumidification cooling heat exchanger (50) flows into the heating reheat heat exchanger (60). In the heating reheat heat exchanger (60), the high temperature and high pressure refrigerant gas passing through the first three-way valve (35) in the a-> b direction is heat-exchanged with the air according to the temperature set in the third temperature regulator (213) Is finally heated and humidified and then supplied to the indoor space (12). Through this process, the outside air is cooled and humidified at a temperature of 16 ° C and a humidity of 95% at a temperature of 20 ° C to 24 ° C and a humidity of 50%, and is supplied to the interior space 12.

On the other hand, a case where the temperature of the outside air is maintained at 10 DEG C or less in winter is defined as a fourth operation mode and explained. The fourth mode of operation is, for example, to operate to keep the air in the room at 50% relative humidity at 20 캜 when the temperature of the outside air is 10 캜 and the humidity is 95%. In this case, the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) are not operated, and the heating reheat heat exchanger (60) operates at 100% efficiency.

Referring to FIGS. 9 and 10, the blower 15 operates to blow outside air into the indoor space. The outside air passes through the outside dehumidifying cooling heat exchanger (40), the second dehumidification cooling heat exchanger (50), and the heating reheat heat exchanger (60) sequentially along the outside air introduction path (11) (12). In this process, we explain in detail how the air and refrigerant exchange heat. The first compressor (21) and the second compressor (22) are operated proportionally according to the required capacity to discharge refrigerant gas of high temperature and high pressure toward the four-way valve (30). For example, both the first compressor (21) and the second compressor (22) are used as a heat source for the heating reheat heat exchanger (60). The high-temperature, high-pressure refrigerant gas discharged from the first compressor (21) and the second compressor (22) flows into the four-way valve (30) Flows in the direction a - > b from (35). The refrigerant flowing from the first three-way valve (35) to the heating reheat heat exchanger (60) is supplied to the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) Let the humidity reach the target temperature and humidity. In this process, the first three-way valve 35 proportionally controls the flow of the refrigerant in the directions a -> b and a-> c according to the temperature set in the third temperature controller 213. The refrigerant passing through the first three-way valve (35) and passing through the heating reheat heat exchanger (60) is liquefied and reaches the point (b). The refrigerant bypassed by the heating reheat heat exchanger is merged at the point of b in the gaseous state. After the temperature of the indoor space is adjusted by the above process, the refrigerant joins the refrigerant at point b and flows into the second three-way valve 70. The second three-way valve 70 flows in a direction a -> b or a -> c depending on the temperature value set in the fourth temperature regulator 214. When the refrigerant is equal to or higher than the set value of the fourth temperature regulator 214, it flows in the direction a -> b. When the refrigerant is lower than the set value of the fourth temperature regulator 214, it flows in the direction a -> c. The refrigerant that has passed through the second three-way valve 70 in the direction a -> b flows into the third external heat exchanger 93 and the fourth external heat exchanger 94. In the third external heat exchanger (93) and the fourth external heat exchanger (94), the external air heat source and the refrigerant undergo heat exchange. In this process, the third external heat exchanger (93) is controlled by the fifth temperature regulator (215) to be blown by the blower fan of the external air blown by the inverter motor, and the fourth external heat exchanger (94) 6 The amount of blowing of the outside air is controlled by the temperature controller 216 to the blowing fan operated by the inverter motor. As a result, the refrigerant is phase-changed into the liquid state, merges at the boiling point, and flows into the receiver tank 80 through the boiling point. On the other hand, the refrigerant flowing in the direction of a - > c from the second three-way valve 70 passes through the third outdoor heat exchanger 93 and the fourth outdoor heat exchanger 94, (80).

The liquid refrigerant flowing into the receiver tank 80 flows through the dryer 85 and the sight glass 86, passing through the point ⓒ, and flowing into the outlet. In this process, the first electromagnetic valve 100, the second electromagnetic valve 103, and the third electromagnetic valve 106 are kept closed. Therefore, the refrigerant does not flow into the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50). As a result, in the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50), heat exchange between the outside air and the refrigerant does not occur. As a result, the temperature of the outside air passing through the first dehumidification cooling heat exchanger (40) and the second dehumidification cooling heat exchanger (50) is maintained at 10 ° C or lower and the humidity is maintained at 95%.

At this time, half of the refrigerant passing through the boiling point passes through the sixth solenoid valve 140, the sixth expansion valve 142, the seventh solenoid valve 144 and the seventh solenoid valve 144 while being thermally expanded, And then flows into the third external heat exchanger (93) through the dew point. Further, the remainder of the refrigerant passing through the point passes through the point, passes through the eighth solenoid valve 147, the eighth expansion valve, the ninth solenoid valve 150 and the ninth expansion valve 152, And then flows into the fourth external heat exchanger 94 through the dew point. The refrigerant is heat-exchanged with the external air heat source at the third external heat exchanger 93 and the fourth external heat exchanger 94 to be superheated steam of low temperature and low pressure and merges at a point to form the four- Liquid separator 26, and the gaseous refrigerant flows into the suction port side of the compressor 20, thereby completing the refrigeration cycle.

In this process, the air introduced into the outside air introducing passage 11 passes through the heating reheat heat exchanger 60 (not shown) in a state where heat is not exchanged with the refrigerant in the first dehumidifying cooling heat exchanger 40 and the second dehumidification cooling heat exchanger 50 ). In the heating reheat heat exchanger (60), the high temperature and high pressure refrigerant gas passing through the first three-way valve (35) in the a-> b direction is heat-exchanged with the air according to the temperature set in the third temperature regulator (213) Is finally heated and humidified and then supplied to the indoor space (12). Through this process, the outside air is cooled and humidified at a temperature of 20 ° C and a humidity of 50% from a state of a temperature of 10 ° C and a humidity of 95%, and is supplied to the interior space 12.

The entire outside air introduction type constant temperature dehumidifying air conditioning system equipped with the evaporation pressure compensation structure according to the present invention is configured to maintain the constant temperature and humidity by introducing the entire outside air for constant temperature and humidity in the indoor space, There is an effect that the harmful substances are not accumulated in the air. The entire outside air introduction type constant temperature dehumidifying air conditioning system provided with the evaporation pressure compensation structure according to the present invention is characterized in that the evaporation pressure of the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger is controlled by the high temperature high pressure refrigerant gas Exchanging the refrigerant with the refrigerant flowing through the main refrigerant pipe in the heat exchanger to compensate for the effect of maintaining a constant constant temperature and humidity effect. Also, as in the preferred embodiment of the present invention, when the control modules for automatically controlling the main valves constituting the present system are provided, the stable constant temperature and humidity effect can be maintained automatically and automatically during the year regardless of seasonal changes.

While the present invention has been described with reference to the preferred embodiments, it is to be understood that the invention is not to be limited by the example, and various changes and modifications may be made without departing from the spirit and scope of the invention.

10: Constant temperature and humidity air conditioning system
11: outside introduction route
12: Indoor space
13: By exhaust path
15: Blower
20: Compressor
21: first compressor
22: Second compressor
24: oil separator
26: a gas-liquid separator
30: Four way valve
35: First three-way valve
40: First dehumidification cooling heat exchanger
45: Main refrigerant tube
47: Evaporative pressure compensation refrigerant tube
50: Second dehumidification cooling heat exchanger
60: Heating reheat heat exchanger
62: auxiliary heating coil
70: second three-way valve
75: Third three-way valve
80: Receiver tank
85: Dryer
86: Sight glass
93: Third external heat exchanger
94: fourth external heat exchanger
100: first solenoid valve
101: first expansion valve
103: second solenoid valve
104: second expansion valve
106: third solenoid valve
107: third expansion valve
110: Third three-way valve
118: fourth solenoid valve
120: Fourth expansion valve
128: fifth solenoid valve
130: fifth expansion valve
140: Sixth solenoid valve
142: Sixth expansion valve
144: seventh solenoid valve
146: Seventh expansion valve
147: Eighth solenoid valve
148: Eighth expansion valve
150: Ninth solenoid valve
152: 9th expansion valve
160: the tenth solenoid valve
170: eleventh solenoid valve
200: Outdoor sensor
211: first temperature regulator
212: second temperature regulator
213: third temperature regulator
214: fourth thermostat
215: fifth thermostat
216: sixth temperature regulator
218: Temperature and humidity sensor
311: first control module
312: second control module
313: Third control module
314: fourth control module
315: fifth control module

Claims (2)

A constant temperature and humidity system that keeps the temperature and humidity of a certain indoor space constant,
An outside air introducing passage for introducing outside air into the entire interior space;
An exhaust path for exhausting the air in the indoor space to the outside; And
And a blower installed in the outside air introduction passage for blowing outside air into the room,
A first dehumidification cooling heat exchanger configured to cool and dehumidify the air introduced into the room through the outside air introduction path by heat exchange with the refrigerant;
A second dehumidification cooling heat exchanger configured to cool and dehumidify the air passing through the first dehumidification cooling heat exchanger by heat exchange with the refrigerant; And
And a heating reheat heat exchanger configured to heat and humidify the air passing through the second dehumidification cooling heat exchanger with the high temperature refrigerant gas,
Wherein the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger each include an evaporation pressure compensating refrigerant tube disposed inside the main refrigerant tube through which the low temperature refrigerant flows and in which the high temperature refrigerant flows in a spiral form,
At least two compressors for sucking refrigerant gas of low temperature and low pressure and discharging refrigerant gas of high temperature and high pressure;
A four-way valve for switching the flow of the refrigerant discharged from the compressor;
A first three-way valve for proportionally distributing the high-temperature and high-pressure refrigerant gas supplied from the four-way valve to pass through the heating reheat heat exchanger or bypass the heating reheat heat exchanger;
A second heat exchanger provided in an end portion of a flow path through which the refrigerant which has been heat-exchanged with the air of the outside air introduction passage in the heating reheat heat exchanger and then liquefied and the refrigerant of high temperature and high pressure bypassing the heating reheat heat exchanger from the first three- Three-way valve;
A receiver tank connected to the second three-way valve through a flow path to temporarily receive the refrigerant;
A third external heat exchanger and a fourth external heat exchanger connected to the second three-way valve by a flow path to cool the refrigerant by heat exchange with an external air heat source and connected to the receiver tank and the flow path,
A drier and a sight glass sequentially disposed on a flow path of the refrigerant discharged from the receiver tank;
The refrigerant having passed through the sight glass is branched into two flow paths so that one flow path is connected to the first dehumidification cooling heat exchanger through the first electromagnetic valve and the first expansion valve and the remaining flow path is connected to the second solenoid valve, Valve, a third solenoid valve, and a third expansion valve to the second dehumidification cooling heat exchanger;
The refrigerant that is heat-exchanged with the air of the outside air introduction path in the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger is connected so as to join the four-way valve and the flow path connected to the suction port side of the compressor;
A third three-way valve disposed in a flow path branched on a flow path connecting the discharge port side of the compressor and the four-way valve;
One of the flow paths branched from the third three-way valve is connected to a flow path connecting the four-way valve and the first three-way valve, and the other is connected to a flow path connecting the first dehumidification cooling heat exchanger and the second dehumidification cooling heat exchanger Branched refrigerant pipe;
The refrigerant having passed through the evaporation pressure compensating refrigerant pipe of the first dehumidifying cooling heat exchanger is connected to flow into the fourth external heat exchanger through the fourth solenoid valve and the fourth expansion valve;
The refrigerant passing through the evaporation pressure compensating refrigerant pipe of the second dehumidification cooling heat exchanger is connected to flow into the third external heat exchanger through the fifth solenoid valve and the fifth expansion valve;
The refrigerant flowing into the fourth external heat exchanger through the fourth expansion valve and the refrigerant flowing into the third external heat exchanger through the fifth expansion valve are connected to flow to the four-way valve;
A second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger; a second dehumidification cooling heat exchanger;
And the sixth solenoid valve is connected to the third external heat exchanger among the auxiliary flow paths. A sixth expansion valve, a seventh solenoid valve, and a seventh expansion valve,
And an eighth solenoid valve, an eighth solenoid valve, a ninth solenoid valve, and a ninth solenoid valve are disposed in a flow path of the auxiliary flow path connected to the fourth external heat exchanger. Constant temperature and humidity air conditioning system. delete

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