JP3874624B2 - Heat pump and dehumidifying air conditioner - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat pump and a dehumidifying air conditioner, and more particularly to a heat pump having a high coefficient of operation (COP) and a dehumidifying air conditioner having such a heat pump and a high dehumidifying capacity per energy consumption.
[0002]
[Prior art]
The configuration of a conventional air conditioning system is shown in FIG. As shown in FIG. 8, a conventional dehumidifying air conditioner includes a compressor 201 that compresses refrigerant, a condenser 202 that condenses the refrigerant compressed by the compressor 201 with outside air OA, and an expansion valve 203 that condenses the condensed refrigerant. The evaporator 204 that depressurizes and evaporates the refrigerant to cool the processing air from the air-conditioned space 100 to a dew point temperature or lower, and the processing air cooled to the dew point or lower on the downstream side of the condenser 202 upstream of the expansion valve 203. And a reheater 205 for reheating with the refrigerant on the side. The compressor 201, the condenser 202, the reheater 205, the expansion valve 203, and the evaporator 204 constitute a heat pump HP that pumps heat from the process air flowing through the evaporator 204 to the outside air OA flowing through the condenser 202.
[0003]
FIG. 9 is a Mollier diagram of a heat pump HP when HFC134a is used as a refrigerant in a conventional dehumidifying air conditioner. In FIG. 9, a point a indicates the state of the refrigerant evaporated by the evaporator 204, and the refrigerant at this time is in a saturated gas state. The refrigerant pressure is 0.34 MPa, the temperature is 5 ° C., and the enthalpy is 400.9 kJ / kg. Point b shows a state where the gas is sucked and compressed by the compressor 201, that is, a state at the discharge port of the compressor 201, and the refrigerant at this time is in a superheated gas state.
[0004]
The refrigerant gas in the state of point b is cooled in the condenser 202 and reaches the state indicated by point c. The refrigerant at this time is in a saturated gas state, the pressure is 0.94 MPa, and the temperature is 38 ° C. The refrigerant is further cooled and condensed under this pressure to reach the state indicated by point d. The refrigerant at this time is in a saturated liquid state, and its pressure and temperature are the same as the pressure and temperature at point c. The enthalpy at this time is 250.5 kJ / kg.
[0005]
The refrigerant liquid is depressurized by the expansion valve 203 and is depressurized to 0.34 MPa, which is a saturation pressure at a temperature of 5 ° C., and reaches a state indicated by a point e. The refrigerant in the state of point e reaches the evaporator 204 as a mixture of a refrigerant liquid and a gas at 5 ° C., takes heat from the processing air in the evaporator 204 and evaporates to become a saturated gas in the state shown by the point a. . This saturated gas is again sucked into the compressor 201, and the above-described cycle is repeated.
[0006]
FIG. 10 is a moist air diagram showing an air conditioning cycle in a conventional dehumidifying air conditioner. In FIG. 10, symbols K, L, and M correspond to the path states denoted by the respective symbols in FIG. As shown in FIG. 10, in the conventional dehumidifying air conditioner, the air (state K) from the conditioned space 100 is cooled below the dew point temperature by the evaporator 204, and the dry bulb temperature decreases and the absolute humidity decreases. State L is reached. This state L is on the saturation line in the wet air diagram. The air in the state L is reheated by the reheater 205, the dry bulb temperature rises while the absolute humidity is constant, reaches the state M, and is supplied to the conditioned space 100. In this state M, both absolute humidity and dry bulb temperature are lower than in state K.
[0007]
[Problems to be solved by the invention]
However, in the conventional dehumidifying air conditioner described above, since there is a large amount of cooling to the dew point, about 30% of the refrigeration effect in the evaporator of the heat pump is consumed to take away the sensible heat load, and the dehumidifying capacity per power consumption (Dehumidification performance) was low. Further, when a single-stage compressor is used as the compressor of the heat pump, it becomes a compression refrigeration cycle of one-stage compression, has a low operating coefficient (COP), and a large amount of power consumption per dehumidification amount.
[0008]
The present invention has been made in view of the above-described problems of the prior art, and an object thereof is to provide a heat pump having a high coefficient of operation (COP) and a dehumidifying air conditioner having a high dehumidifying capacity per energy consumption.
[0009]
[Means for Solving the Problems]
In order to solve such problems in the prior art, an aspect of the present invention includes a booster that pressurizes a refrigerant, a condenser that condenses the refrigerant and heats a high heat source fluid, and evaporates the refrigerant. An evaporator that cools the low heat source fluid and a refrigerant path between the condenser and the evaporator, and the refrigerant is supplied at a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator. A first heat exchanging means for evaporating and cooling the low heat source fluid; a refrigerant path between the condenser and the evaporator; and a condensation pressure of the condenser and an evaporation pressure of the evaporator The second heat exchange means for condensing the refrigerant with the intermediate pressure to heat the low heat source fluid, the first heat exchange means, the evaporator, and the second heat exchange means are connected in this order. A low heat source fluid path, and the refrigerant path is located downstream of the condenser. After passing through the second heat exchange means Te, a heat pump, characterized in that through the said first heat exchange means the second heat exchange means alternately.
[0010]
According to another aspect of the present invention, a booster that pressurizes the refrigerant, a condenser that condenses the refrigerant and heats the processing air, and evaporation that evaporates the refrigerant and cools the processing air to a dew point temperature or less. And in the refrigerant path between the condenser and the evaporator, the refrigerant is evaporated at a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator to cool the processing air. Provided in a refrigerant path between the first heat exchanging means and the condenser and the evaporator to condense the refrigerant at a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator. A second heat exchange means for heating the treatment air, a treatment air path for connecting the first heat exchange means, the evaporator and the second heat exchange means in this order, and a refrigerant path Passed through the second heat exchange means downstream of the condenser A dehumidifying air-conditioning apparatus, characterized in that through the said first heat exchange means the second heat exchange means alternately.
[0011]
With such a configuration, the low heat source fluid can be precooled in the first heat exchanging means before cooling in the evaporator, and the heat of the precooling is used in the second heat exchanging means after cooling in the evaporator. Provided is a dehumidifying air conditioner that consumes less energy per dehumidifying amount by heating the low heat source fluid, using the processing air as a low heat source, and cooling the processing air below the dew point temperature with an evaporator. It becomes possible.
[0012]
In addition, since the refrigerant liquid exiting the condenser first flows into the condensing section and is condensed there, the dryness of the refrigerant serving as a heat medium in each heat exchange means is generally low, that is, close to wet saturated steam. Heat exchange. Therefore, even when the flow rate of the refrigerant is reduced by the capacity control at the partial load, the ratio of the refrigerant vapor flowing into the evaporator can be reduced, and the dehumidification capacity per power consumption is less lowered even at the partial load. It can be set as a dehumidification air conditioner.
[0013]
In a preferred aspect of the present invention, the refrigerant path has an evaporation section in the first heat exchange means and a condensation section in the second heat exchange means, and the second heat exchange means. The first condensing section has a larger heat transfer area than the first evaporating section in the first heat exchange means.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of a dehumidifying air conditioner according to the present invention will be described with reference to FIGS. 1 to 6. FIG. 1 is a diagram showing an overall configuration of an air conditioning system in the present embodiment, and FIG. 2 is a diagram schematically showing a flow in a dehumidifying air conditioner in the present embodiment. The dehumidifying air conditioner in the present embodiment cools and dehumidifies the air (process air) RA in the air-conditioned space 100 below its dew point temperature, and includes a heat pump HP1 inside. The treated air SA whose humidity has been lowered by the dehumidifying air conditioner is returned to the conditioned space 100, whereby the conditioned space 100 is maintained in a comfortable environment.
[0015]
As shown in FIG. 1, the dehumidifying air conditioner basically includes an indoor unit 10 installed in the air-conditioned space 100 and an outdoor unit 20 installed outside (outdoor) the air-conditioned space 100. The indoor unit 10 of the dehumidifying air conditioner includes a refrigerant evaporator 1 that evaporates the refrigerant, a heat exchanger 2 that performs heat exchange between the refrigerant and the processing air, and a blower 3 that circulates the processing air. Yes. The heat exchanger 2 performs heat exchange indirectly between the processing air before and after flowing into the evaporator 1 via a refrigerant, and first heat that evaporates the refrigerant and cools the processing air. An exchange unit 21 and a second heat exchange unit 22 that condenses the refrigerant and heats the processing air are provided. The outdoor unit 20 of the dehumidifying air conditioner includes a booster 4 that compresses the refrigerant, a refrigerant condenser 5 that cools and condenses the refrigerant, and a blower 6 that blows cooling air.
[0016]
As shown in FIG. 2, the path through which the processing air flows (processing air path) includes a path 30 connecting the air-conditioned space 100 and the first heat exchange unit 21 of the heat exchanger 2, and a first heat exchange unit. 21, a path 31 connecting the evaporator 1 to the evaporator 1, a path 32 connecting the evaporator 1 and the second heat exchange part 22 of the heat exchanger 2, and a connection between the second heat exchange part 22 and the blower 3. And a path 34 that connects the blower 3 and the air-conditioned space 100. The first heat exchanging part 21 of the heat exchanger 2, the evaporator 1 and the second heat exchanging part 22 of the heat exchanger 2 are sequentially connected by such a processing air path.
[0017]
On the other hand, as shown in FIG. 2, the refrigerant path through which the refrigerant flows is a path 40 that connects the evaporator 1 and the booster 4, a path 41 that connects the booster 4 and the condenser 5, and the condenser 5. And a path 42 connecting the heat exchanger 2 and a path 43 connecting the heat exchanger 2 and the evaporator 1. On the downstream side of the condenser 5, the refrigerant path first passes through the second heat exchange unit 22, and then alternately passes through the first heat exchange unit 21 and the second heat exchange unit 22. In the first heat exchanging part 21, an evaporating section 61 for cooling the air K flowing through the first heat exchanging part 21 by evaporating the refrigerant is formed, and in the second heat exchanging part 22, A condensing section 62 is formed that heats the air L flowing through the second heat exchange unit 22 by condensing the refrigerant. A throttle 50 is disposed in the refrigerant path 42 upstream of the second heat exchange unit 22 of the heat exchanger 2, and a throttle 51 is disposed in the refrigerant path 43 downstream of the second heat exchange unit 22. ing. As these throttles 50 and 51, for example, an orifice, a capillary tube, an expansion valve, or the like can be used.
[0018]
Further, outside air OA as cooling air is introduced into the condenser 5 via a path 46. The outside air OA takes heat from the refrigerant that condenses, and the heated outside air is sucked into the blower 6 via the path 47 and discharged to the outside via the path 48 (EX).
[0019]
FIG. 3 is an enlarged view showing a refrigerant path in the heat exchanger 2 of the dehumidifying device of FIG. The refrigerant path including the evaporation section 61 and the condensing section 62 first passes through the second heat exchanging portion 22 while meandering, and then the first heat exchanging portion 21 and the second heat exchanging portion. The portions 22 are alternately and repeatedly penetrated. That is, as shown in FIG. 3, the refrigerant path in the heat exchanger 2 includes, in order from the condenser 5, the condensing sections 62a to 62d, the evaporating sections 61a and 61b, the condensing sections 62e and 62f, and the evaporating sections 61c and 61d. And a condensing section 62g. Here, the first condensing section (62a to 62d) in the second heat exchanging section 22 has a larger heat transfer area than the first evaporating sections (61a and 61b) in the first heat exchanging section 21. Yes.
[0020]
A serpentine heat exchanger can be used as such a heat exchanger. 4A is a plan view showing a serpentine type heat exchanger used in the heat exchanger of the dehumidifying air conditioner of FIG. 2, and FIG. 4B is a cross-sectional view taken along line AA of FIG. 4A. It is. As shown in FIGS. 4A and 4B, the first heat exchanging portion 21 that flows the air K before passing through the evaporator 1 and the first heat exchange portion 21 that flows air L after passing through the evaporator 1 are used. The two heat exchange sections 22 are accommodated in separate rectangular parallelepiped spaces, and in these rectangular parallelepiped spaces, a plurality of heat exchange tubes 70 are arranged in parallel as refrigerant paths on a plane orthogonal to the air flow. ing. The refrigerant paths in each heat exchange section in FIGS. 2 and 3 are illustrated in a simplified manner for convenience, but typically, as shown in FIG. A tube 70 is used.
[0021]
As shown in FIG. 4B, the heat exchange tube 70 is a flat tube having a plurality of flow passage chambers 71 formed therein, and such a heat exchange tube is formed by extrusion molding of aluminum. . A plurality of aluminum fins 72 are provided between the heat exchange tubes 70 in each row. And as shown to Fig.4 (a), the thin tube group comprised by such a heat exchange tube 70 is meandering the inside of the heat exchanger 2, and the 1st heat exchange part 21 and the 2nd heat exchange part. It passes through the inside of 22 and is comprised so that high temperature air and low temperature air may contact alternately.
[0022]
As shown in FIGS. 1 and 2, a drain pan 7 is provided inside the indoor unit 10 of the dehumidifying air conditioner. The drain pan 7 is not only located in the evaporator 1 but also below the heat exchanger 2. It is preferable to provide a cover. In the first heat exchanging part 21 of the heat exchanger 2, the processing air is mainly precooled. However, since some moisture may condense here, it is particularly provided below the first heat exchanging part 21. preferable.
[0023]
Next, the flow of the refrigerant between the devices will be described with reference to FIGS.
The refrigerant gas compressed by the booster 4 is led to the condenser 5 via the refrigerant gas pipe 41 connected to the discharge port of the booster 4, and is cooled and condensed by the outside air OA as cooling air. The refrigerant liquid exiting the condenser 5 is decompressed and expanded by the throttle 50, and a part of the refrigerant liquid is evaporated (flashed). The refrigerant in which the liquid and gas are mixed reaches the condensing section 62a of the second heat exchanging unit 22, where the refrigerant liquid flows so as to wet the inner wall of the tube of the condensing section 62a. Although the liquid phase refrigerant flows into the condensing section 62a, the refrigerant flowing into the condensing section 62a may be a refrigerant liquid that is partially vaporized and that includes a slight gas phase. While flowing through the refrigerant condensing section 62a, the process air cooled and dehumidified by the evaporator 1 is heated (reheated), and the refrigerant itself is deprived of heat and condensed.
[0024]
Since the refrigerant path in the heat exchanger 2 is constituted by a series of tubes, the refrigerant liquid condensed in the condensation section 62a flows into the condensation sections 62b, 62c and 62d. While the refrigerant flows through the condensing sections 62b, 62c, and 62d, heat is further deprived by the low-temperature processing air, and the vapor-phase refrigerant is further condensed.
[0025]
The refrigerant liquid condensed in the condensation sections 62a to 62d flows into the evaporation section 61a of the first heat exchange unit 21. In the evaporation section 61a, the processing air before flowing into the evaporator 1 is cooled (precooled), and the refrigerant itself is heated to increase the gas phase. The refrigerant gas evaporated in the evaporation section 61a (and the refrigerant liquid that has not evaporated) flows into the evaporation section 61b, and the processing air before flowing into the evaporator 1 is cooled (pre-cooled) while flowing through the evaporation section 61b, The refrigerant itself is further heated to increase the gas phase.
[0026]
The refrigerant gas evaporated in the evaporation sections 61a and 61b flows into the next condensation section 62e and the subsequent condensation section 62f, and the processing air before flowing into the evaporator 1 is heated (reheated) in the same manner as described above. The Further, the refrigerant gas flows into the evaporating section 61c and the condensing section 62d, and the processing air is cooled (pre-cooled). In this way, the refrigerant flows through the refrigerant path in the heat exchanger while undergoing a phase change between the gas phase and the liquid phase, and the processing air before being cooled by the evaporator 1 and the absolute humidity by being cooled by the evaporator 1. Heat exchange is indirectly performed with the lowered processing air.
[0027]
Here, the refrigerant liquid exiting the condenser 5 first flows into the condensing sections 62a to 62d and is condensed there, so that the degree of dryness of the refrigerant serving as the heat medium in the heat exchanger 2 is generally reduced, that is, Heat exchange can be performed close to wet saturated steam. Therefore, even when the flow rate of the refrigerant is reduced by capacity control at the time of partial load, the rate at which the refrigerant vapor passes through the throttle 51 (gas bypass) can be reduced, and dehumidification per power consumption even at the time of partial load. It can be set as the dehumidification air conditioner with little fall of capability.
[0028]
The refrigerant liquid condensed in the final condensing section 62e is depressurized and expanded by the throttle 51 disposed on the downstream side of the second heat exchanging section 22, and the temperature decreases. Then, the refrigerant reaches the evaporator 1 and evaporates in the evaporator 1. The processing air X that has passed through the first heat exchange unit 21 is cooled by the evaporation heat of the refrigerant. The refrigerant evaporated and gasified by the evaporator 1 is guided to the suction side of the booster 4. Then, the above cycle is repeated.
[0029]
Next, the effect | action of heat pump HP1 contained in the dehumidification air conditioner in this embodiment is demonstrated. FIG. 5 is a refrigerant Mollier diagram of the heat pump HP1 included in the dehumidifying air conditioner of FIG. In the diagram shown in FIG. 5, HFC134a is used as the refrigerant, and the horizontal axis represents enthalpy and the vertical axis represents pressure. Not only HFC134a but also HFC407C and HFC410A can be used as refrigerants, and when these refrigerants are used, the operating pressure region shifts to a higher pressure side than in the case of HFC134a.
[0030]
In FIG. 5, the point a shows the state of the refrigerant evaporated in the evaporator 1 of FIG. 2, and the refrigerant at this time is in a saturated gas state. The pressure of the refrigerant is 0.350 MPa, the temperature is 5 ° C., and the enthalpy is 401.5 kJ / kg. Point b shows the state in which this gas is sucked and compressed by the booster 4, that is, the state at the discharge port of the booster 4, and the refrigerant at this time has a pressure of 0.963 MPa and is in a superheated gas state. .
[0031]
The refrigerant gas in the state of point b is cooled in the condenser 5 and reaches the state indicated by point c. The refrigerant at this time is in a saturated gas state, the pressure is 0.963 MPa, and the temperature is 38 ° C. The refrigerant is further cooled and condensed under this pressure to reach the state indicated by point d. The refrigerant at this time is in a saturated liquid state, and its pressure and temperature are the same as the pressure and temperature at point c. The enthalpy at this time is 253.4 kJ / kg.
[0032]
The refrigerant liquid is depressurized by the throttle 50 and flows into the condensing section 62 a of the second heat exchange unit 22. The state at this time is indicated by a point e, in which a part of the liquid is evaporated and the liquid and the gas are mixed. The pressure at this time is an intermediate pressure between the condensing pressure of the condenser 5 and the evaporating pressure of the evaporator 1, and is a value between 0.963 MPa and 0.350 MPa in the present embodiment.
[0033]
Then, in the condensing section 62a and the condensing sections 62b to 62d that follow, the refrigerant liquid is condensed under the intermediate pressure, and a state of a point f1 located on the saturated liquid line is obtained. The refrigerant at this time is in a saturated liquid state. And the refrigerant | coolant of the state shown by the point f1 flows in into the evaporation sections 61a and 61b. In the evaporating sections 61a and 61b, the refrigerant liquid evaporates to a state of a point g1 located between the saturated liquid line and the saturated gas line. In this state, a part of the liquid is evaporated, but a considerable amount of the refrigerant liquid remains.
[0034]
The refrigerant in the state of the point g1 flows into the condensing sections 62e and 62f, and the refrigerant increases the liquid phase to reach the state of the point f2. The point f2 is located on the saturated liquid line in the Mollier diagram. The refrigerant in the state at the point f2 flows into the evaporation sections 61c and 61d, where heat is taken away to reach the state at the point g2, and further flows into the condensing section 62g. In the condensing section 62g, the refrigerant increases the liquid phase and reaches the state of the point f3. The point f3 is located on the saturated liquid line in the Mollier diagram. At this time, the temperature of the refrigerant is 18 ° C., and the enthalpy is 224.7 kJ / kg.
[0035]
The refrigerant liquid in the state of the point f3 is decompressed by the throttle 51 to 0.350 MPa, which is a saturation pressure at a temperature of 5 ° C., and reaches the state indicated by the point h. The refrigerant in the state at the point h reaches the evaporator 1 as a mixture of a refrigerant liquid and a gas at 5 ° C., where heat is taken from the processing air and evaporated to become a saturated gas as indicated by the point a. This saturated gas is again sucked into the booster 4, and the above-described cycle is repeated.
[0036]
Thus, in the heat exchanger 2, the refrigerant undergoes a change in evaporation state such as from the point f 1 to the point g 1 or from the point f 2 to the point g 2 in the evaporation section 61, and from the point e to the point f 1 in the condensation section 62. Since the state of condensation is changed from point g1 to point f2 or from point g2 to point f3, evaporative heat transfer and condensation heat transfer are performed, the heat transfer rate is very high, and heat exchange High efficiency.
[0037]
Here, when considered as a compression heat pump HP1 including the booster 4, the condenser 5, the throttles 50 and 51, and the evaporator 1, when the heat exchanger 2 according to the present invention is not provided, the point d in the condenser 5 is Since the refrigerant in the state is returned to the evaporator 1 through the throttle, the enthalpy difference that can be used in the evaporator 1 is only 401.5-253.4 = 148.1 kJ / kg. However, when the heat exchanger 2 according to the present invention is provided, 401.5-224.7 = 176.8 kJ / kg, and the amount of gas circulated to the compressor with respect to the same cooling load is reduced. Can be reduced by 16% (= 1-148.1 / 176.8). That is, it is possible to have the same action as the subcool cycle.
[0038]
6 is a moist air diagram showing an air conditioning cycle in the dehumidifying air conditioner of FIG. In FIG. 6, symbols K, L, M, and X correspond to the path states given the respective symbols in FIG. 2.
The processing air (state K) from the conditioned space 100 is sent to the first heat exchange unit 21 of the heat exchanger 2 through the processing air path 30 and is cooled to some extent by the refrigerant evaporated in the evaporation section 61. The Since this is preliminary cooling before the evaporator 1 cools to the dew point temperature or lower, it can be called precooling. While being precooled in the evaporating section 61, the processing air reaches a point X on the saturation line while removing moisture to some extent and slightly reducing the absolute humidity. Or it is good also as cooling to the intermediate point of the point K and the point X in a pre-cooling stage. Or it is good also as cooling to the point which moved to the low humidity side somewhat on the saturation line beyond the point X.
[0039]
The processing air pre-cooled by the first heat exchange unit 21 is introduced into the evaporator 1 through the path 31. In the evaporator 1, the processing air is cooled below its dew point temperature by the refrigerant that is depressurized by the throttle 51 and evaporated at a low temperature, and the dry bulb temperature is lowered while lowering the absolute humidity while depriving moisture. L is reached. In FIG. 6, the thick line indicating the change from the point X to the point L is drawn out of the saturation line for convenience, but actually overlaps the saturation line.
[0040]
The processing air in the state of the point L flows into the second heat exchange part 22 of the heat exchanger 2 through the path 32 and is heated to the point M by the refrigerant condensed in the condensing section 62 while keeping the absolute humidity constant. It reaches. The point M is air having an appropriate relative humidity whose absolute humidity is sufficiently lower than that of the point K and the dry bulb temperature is not too low. The air in the state of point M is sucked by the blower 3 and returned to the conditioned space 100 through the path 34.
[0041]
Here, in the cycle on the processing air side shown on the wet air diagram of FIG. 6, the amount of heat obtained by pre-cooling the processing air in the first heat exchange unit 21, that is, the processing air is reheated in the second heat exchange unit 22. The amount of heat ΔH is the amount of heat recovery, and the amount of heat obtained by cooling the processing air with the evaporator 1 is ΔQ. The cooling effect for cooling the air-conditioned space 100 is Δi.
[0042]
As described above, in the heat exchanger 2, the processing air is precooled by the evaporation of the refrigerant in the evaporation section 61, and the processing air is reheated by the condensation of the refrigerant in the condensation section 62. The refrigerant evaporated in the evaporation section 61 is condensed in the condensation section 62. Thus, heat exchange between the process air before and after being cooled by the evaporator 1 is indirectly performed by the evaporation and condensation action of the same refrigerant.
[0043]
Thus, in the present embodiment, the same refrigerant is used as the heat transfer medium of the evaporator that cools the processing air below the dew point, the precooler that precools the processing air, and the reheater that performs reheating. Therefore, the refrigerant system is simplified to a single, and the pressure difference between the evaporator and the condenser can be utilized, so that circulation becomes active, and further, the boiling phenomenon with phase change in pre-cooling and reheating heat exchange. Can be applied, so the efficiency can be increased.
[0044]
In the above-described embodiment, the outside air OA as the cooling air is heated using the condenser. However, the air heated in the second heat exchange unit is further heated (reheated) using the condenser. Also good. FIG. 7 shows a configuration in the case where the air heated by the second heat exchange unit 22 is heated (reheated) by the condenser 5 and supplied to the conditioned space 100 in the dehumidifying air conditioner of the above-described embodiment. An example is shown. In addition, in the example of FIG. 7, although the air blower 3 is installed between the evaporator 1 and the heat exchanger 2, it is not restricted to this position.
[0045]
Although one embodiment of the present invention has been described so far, the present invention is not limited to the above-described embodiment, and may be implemented in various forms within the scope of the technical idea. For example, the number of evaporation sections in the first heat exchange section and the number of condensation sections in the second heat exchange section of each refrigerant path are not limited to those shown in the figure. Further, in the above-described embodiment, the dehumidifying device that air-conditions the air-conditioned space has been described as an example. .
[0046]
【The invention's effect】
As described above, according to the present invention, the low heat source fluid can be pre-cooled in the first heat exchange means before cooling in the evaporator, and the second heat is used after the cooling in the evaporator. Since the low heat source fluid can be heated in the heat exchanging means, it is possible to provide a dehumidifying air conditioner with a small energy consumption per dehumidifying amount.
[0047]
In addition, since the refrigerant liquid exiting the condenser first flows into the condensing section and is condensed there, the dryness of the refrigerant serving as a heat medium in each heat exchange means is generally low, that is, close to wet saturated steam. Heat exchange. Therefore, even when the flow rate of the refrigerant is reduced by the capacity control at the partial load, the ratio of the refrigerant vapor flowing into the evaporator can be reduced, and the dehumidification capacity per power consumption is less lowered even at the partial load. It can be set as a dehumidification air conditioner.
[Brief description of the drawings]
FIG. 1 is a diagram showing an overall configuration of a dehumidifying air conditioning system according to the present invention.
FIG. 2 is a diagram schematically showing a flow in a dehumidifying air conditioner according to an embodiment of the present invention.
FIG. 3 is an enlarged view showing a refrigerant path in the heat exchanger of the dehumidifying air conditioner of FIG. 2;
4 is a diagram showing a specific example of a serpentine type heat exchanger used in the heat exchanger of the dehumidifying air conditioner of FIG. 2. FIG.
5 is a refrigerant Mollier diagram of a heat pump included in the dehumidifying air conditioner of FIG. 2. FIG.
6 is a moist air diagram showing an air conditioning cycle in the dehumidifying air conditioner of FIG. 2; FIG.
FIG. 7 is a diagram schematically showing a flow in a dehumidifying air conditioner according to another embodiment of the present invention.
FIG. 8 is a diagram schematically showing a flow in a conventional dehumidifying air conditioner.
FIG. 9 is a refrigerant Mollier diagram of a heat pump included in a conventional dehumidifying air conditioner.
FIG. 10 is a moist air diagram showing an air conditioning cycle in a conventional dehumidifying air conditioner.
[Explanation of symbols]
1 Evaporator
2 Heat exchanger
3, 6 Blower
4 Booster
5 Condenser
7 Drain pan
10 indoor units
20 Outdoor unit
21 1st heat exchange part
22 2nd heat exchange part
50, 51 aperture
30-34, 40-43, 46-48 routes
61 Evaporation section
62 Condensation section
70 Heat exchange tube
71 Channel room
72 fins
100 Air-conditioned space

Claims (4)

A booster for boosting the refrigerant;
A condenser for condensing the refrigerant to heat the high heat source fluid;
An evaporator for evaporating the refrigerant to cool the low heat source fluid;
Provided in a refrigerant path between the condenser and the evaporator, and evaporates the refrigerant at a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator to cool the low heat source fluid. 1 heat exchange means;
Provided in a refrigerant path between the condenser and the evaporator, and heats the low heat source fluid by condensing the refrigerant with a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator. Two heat exchange means;
A low heat source fluid path connecting the first heat exchange means, the evaporator and the second heat exchange means in this order;
The refrigerant path passes through the second heat exchange means on the downstream side of the condenser, and then alternately passes through the first heat exchange means and the second heat exchange means. . The refrigerant path has an evaporation section in the first heat exchange means and a condensation section in the second heat exchange means,
The heat pump according to claim 1, wherein the first condensing section in the second heat exchanging means has a larger heat transfer area than the first evaporating section in the first heat exchanging means. A booster for boosting the refrigerant;
A condenser for condensing the refrigerant and heating the processing air;
An evaporator for evaporating the refrigerant and cooling the processing air to a dew point temperature or lower;
A first cooling unit is provided in a refrigerant path between the condenser and the evaporator, and evaporates the refrigerant at a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator to cool the processing air. Heat exchange means,
A second refrigerant passage disposed between the condenser and the evaporator, wherein the processing air is heated by condensing the refrigerant with a pressure intermediate between the condensation pressure of the condenser and the evaporation pressure of the evaporator; Heat exchange means,
A processing air path that connects the first heat exchange means, the evaporator, and the second heat exchange means in this order;
The refrigerant path passes through the second heat exchange means on the downstream side of the condenser, and then alternately passes through the first heat exchange means and the second heat exchange means. Air conditioner. The refrigerant path has an evaporation section in the first heat exchange means and a condensation section in the second heat exchange means,
The dehumidifying air conditioner according to claim 3, wherein the first condensing section in the second heat exchanging means has a larger heat transfer area than the first evaporating section in the first heat exchanging means.

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