JP6257645B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner that suppresses a decrease in dehumidification amount while realizing energy saving operation (hereinafter abbreviated as energy saving operation).

  As shown in FIG. 7, a conventional air conditioner compresses and discharges a refrigerant, a condenser 2 that liquefies the refrigerant by heat exchange with external air, and depressurizes the refrigerant from the condenser 2. And an evaporator 8 that evaporates the refrigerant from the expansion valve 3 and cools the use-side air. These components are connected by refrigerant pipes 11, 12, 13A, and 16. Thus, a general refrigerant circuit is configured. In this refrigerant circuit, the compressor 1 compresses the refrigerant into a high-temperature and high-pressure gas state and sends it to the condenser 2, and the condenser 2 condenses the refrigerant into a high-pressure liquid state. The refrigerant from the condenser 2 is sent to the expansion valve 3, expanded by being depressurized by the expansion valve 3, and sent to the evaporator 8 in a gas-liquid two-phase state at a low pressure. A refrigeration cycle operation is performed in which the refrigerant evaporated in the evaporator 8 and turned into a gas state at low pressure is returned to the compressor 1 again. The indoor air temperature is adjusted using such a refrigeration cycle operation. For example, in the cooling operation, the interior of the room is cooled by the evaporator 8. At this time, if the temperature of the refrigerant in the evaporator 8, that is, the evaporation temperature is lower than the dew point temperature of the room air, the room air is subjected to a latent heat treatment, that is, a dehumidification process in the evaporator 8.

The amount of dehumidification at this time increases as the difference between the refrigerant evaporation temperature and the air dew point temperature increases. Conventionally, the amount of dehumidification has been secured by lowering the evaporation temperature of the refrigerant in the evaporator 8 using this property. However, in this method, since the low-pressure side pressure correlated with the evaporation temperature is lowered, the density of the refrigerant sucked into the compressor 1 is lowered and the evaporation capacity is lowered. Therefore, in order to maintain the evaporation capacity, it is necessary to increase the operating frequency of the compressor 1 or increase the displacement volume. As a result, there is a problem that the input to the compressor 1 increases and energy saving operation cannot be realized.

The change in the state of the refrigerant by the conventional air conditioner described above is shown in the Ph diagram of FIG. In FIG. 8, states (a) to (b) to (c) to (i) all indicated by solid lines represent refrigeration cycle operations during energy-saving operation, and are partially indicated by broken lines (a) to (a) to (i). State (b ′) to state (c ′) to state (i) represent the refrigeration cycle operation during normal operation. Here, if the refrigerant circulation rate is Gr = 600 kg / h, the evaporation capacity is Qe = 26.8 kW in the above-described refrigeration cycle operation. Here, when the state (c) is compared with the state (c ′), since the pressure is higher in the state (c), the refrigerant density is higher. Therefore, compared with the refrigeration cycle operation via the state (c ′), the refrigeration cycle operation via the state (c) is an energy saving operation because the operating frequency of the compressor 1 can be lowered. In FIG. 8, the numerical values of the refrigerant pressure and the enthalpy in the refrigerant circuit, which are obtained by experiments, are shown for reference.

Next, FIG. 9 shows changes in the air state caused by the above-described conventional air conditioner. In the air diagram shown in FIG. 9, coordinates A to B indicated by solid lines represent changes in the air state during energy-saving operation, and coordinates A to B ′ indicated by broken lines represent changes in the air state during normal operation. ing. Here, the slopes of the coordinates A to B and the coordinates A to B ′ represent SHF (sensible heat ratio) and are determined by the evaporation temperature. When the air volume is V = 90 m 3 / min, the dehumidification amount is L = 10.4 kg / min at coordinates A to B ′ during normal operation. On the other hand, at coordinates A to B during energy saving operation, the dehumidification amount is L ′ = 5.9 kg / min, which causes a problem that the dehumidification amount is significantly reduced as compared with that during normal operation. In FIG. 9, the numerical values of dry bulb temperature, absolute humidity, and enthalpy obtained in the experiment are shown for reference.

  On the other hand, Patent Document 1 discloses an air conditioner having the same configuration as the air conditioner shown in FIG. In the air conditioner described in Patent Document 1, the latent heat treatment, that is, the dehumidification treatment is performed on the air before flowing into the evaporator 8 in advance by a moisture absorption device, thereby reducing the latent heat treatment load in the evaporator 8 and the evaporation temperature, that is, the low pressure side. Energy saving operation is realized while maintaining the dehumidification amount by suppressing the pressure drop.

JP 2006-308229 A

However, since the air conditioner described in Patent Document 1 uses a hygroscopic device, the system configuration is complicated, and the hygroscopic material used in the hygroscopic device is deteriorated, so it is necessary to replace it in a timely manner. There are concerns about problems such as increased maintenance load and running cost.

  The present invention has been made to solve the above-described problems, and provides an air conditioner having a simple configuration, a small maintenance load, and capable of suppressing a decrease in the dehumidification amount while realizing an energy saving operation. The purpose is that.

An air conditioner according to the present invention includes a compressor that compresses and discharges a refrigerant, a condenser that performs heat exchange between the refrigerant discharged from the compressor and a heat source side fluid, and decompresses the refrigerant from the condenser. And a first evaporator that performs a sensible heat removal process on the use side air by heat exchange with the refrigerant from the expansion valve, and is connected in an annular manner via a refrigerant pipe, Furthermore, a booster mechanism that is disposed in a refrigerant pipe between the expansion valve and the first evaporator, boosts the refrigerant from the expansion valve, and sends it to the first evaporator; the expansion valve and the booster mechanism Provided in the refrigerant pipe between, a branch part for branching the refrigerant decompressed to a saturated liquid state by the expansion valve , a bypass pipe connecting the branch part and the junction part of the pressure increasing mechanism, and provided in the bypass pipe have been saturated from the branch portion And adjusting the expansion valve further depressurizing the refrigerant decompressed by the state, have been deployed in the bypass pipe of the refrigerant flow direction downstream side of the regulating expansion valve, wherein the heat exchange with the refrigerant from the adjustment expansion valve A second evaporator that performs a latent heat removal process on the use-side air from the first evaporator, and the refrigerant decompressed to a saturated liquid state by the expansion valve flows from the branch portion to the bypass pipe and passes through the bypass pipe. Enlarging the enthalpy difference between the state of the refrigerant further depressurized by the adjustment expansion valve and the state of the refrigerant flowing into the refrigerant pipe from the branch portion and being sent out to the pressure increasing mechanism in a saturated liquid state , The acceleration mechanism amplifies the acceleration width of the refrigerant.

In the air conditioner of the present invention, the refrigerant condensed in the condenser is decompressed to the saturated liquid state by the expansion valve, and after the refrigerant is diverted at the branching portion, a part of the refrigerant is pressurized by the pressure increasing mechanism. The remainder of the refrigerant is decompressed by the expansion valve for adjustment, and then flows into the second evaporator where importance is placed on latent heat treatment. After the refrigerant is combined with the refrigerant from the aforementioned branching portion by the pressure-increasing mechanism, importance is placed on sensible heat treatment. Since it is configured to flow into the first evaporator, there is an effect that an excessive decrease in the dehumidification amount can be suppressed without reducing the density of the refrigerant sucked into the compressor, that is, while realizing the energy saving operation. In addition, an air conditioner having a simple configuration and a small maintenance load can be provided.

It is a schematic block diagram which shows the refrigerant circuit of the air conditioner in Embodiment 1 of this invention. It is a figure which shows the ejector used with the said air conditioner, Comprising: (a) is a schematic sectional side view, (b) is a figure of the graph which shows the relationship of the distance of the length direction of an ejector, and a pressure. It is a Ph diagram for demonstrating the state change of the refrigerant | coolant in the said air conditioner. It is an air line figure for demonstrating the state change of the air in the said air conditioner. It is the figure which showed the relationship between the pressure | voltage rise of an ejector by the difference in arrangement | positioning of the 1st evaporator of the said air conditioner, and a 2nd evaporator, total evaporation capability, and total dehumidification amount. It is the figure which showed the relationship between pressure increase of the refrigerant | coolant pressure by the ejector of the said air conditioner, and total dehumidification amount. It is a schematic block diagram which shows the refrigerant circuit of the conventional air conditioner. It is a Ph diagram for demonstrating the state change of the refrigerant | coolant in the conventional air conditioner. It is an air line figure for demonstrating the state change of the air in the conventional air conditioner.

Embodiment 1 FIG.
The first embodiment will be described below. It should be noted that the numerical values and the like appearing in the text are assumed here for convenience of explanation of the operation.
1 is a schematic configuration diagram illustrating a refrigerant circuit of an air conditioner according to Embodiment 1. FIG.
In the figure, the air conditioner according to the first embodiment liquefies the compressor 1 that compresses and discharges the refrigerant and heat exchange between the refrigerant discharged from the compressor 1 and the heat source side fluid (for example, outdoor air). The sensible heat removal process is performed on the use side air by the heat exchange between the condenser 2, the expansion valve 3 that depressurizes the refrigerant from the condenser 2 to bring it into a saturated liquid state, and the refrigerant from the expansion valve 3, and cools it. 1 evaporator 6. The first evaporator 6 and the compressor 1 are connected by a refrigerant pipe 16, the compressor 1 and the condenser 2 are connected by a refrigerant pipe 11, and the condenser 2 and the expansion valve 3 are connected by a refrigerant. The pipes 12 are connected. A refrigerant pipe 13 is connected to the refrigerant outlet side of the expansion valve 3. The front end of the refrigerant pipe 13 is a branch portion 10, and refrigerant pipes 14 and 17 are branched and connected to the branch portion 10. The front end of the refrigerant pipe 14 is connected to the connecting pipe part 5E of the nozzle part 5D of the ejector 5 (an example of a pressure increasing mechanism). The outlet side of the diffuser portion 5C of the ejector 5 is connected to the first evaporator 6 via the refrigerant pipe 15. The outlet side of the first evaporator 6 is connected to the suction side of the compressor 1 through a refrigerant pipe 16. On the other hand, the bypass pipe 17 branched from the branch section 10 is connected to the adjustment expansion valve 4, and the adjustment expansion valve 4 is connected to the second evaporator 7 via the bypass pipe 18. Further, the second evaporator 7 is connected to the connecting pipe portion 5F of the merging portion 5A through the bypass pipe 19.

In this Embodiment 1, the 1st evaporator 6 and the 2nd evaporator 7 are comprised integrally. That is, a pipe between the refrigerant pipes 15 and 16 is arranged on the front side in an integral casing (not shown) having a front opening and a rear opening, and a pipe between the bypass pipes 18 and 19 is arranged on the rear side of this pipe. Yes. Each pipe extends in the left-right direction and has a reciprocating arrangement in which a plurality of lines are folded back. These pipes are supported by a number of fins (not shown) spaced apart in the left-right direction. These fins are arranged so that air can be ventilated in the direction indicated by the arrow W in FIG. The first evaporator 6 and the second evaporator 7 having such an integrated structure are arranged in the air passage 9 </ b> A of the air passage casing 9 and are ventilated by driving the blower 20.

As shown in FIG. 2 (a), the ejector 5 is provided in a tubular box-like joining portion 5A having a connecting pipe portion 5F connected to the bypass pipe 19 from the second heat exchanger 7, and is provided through the joining portion 5A. In addition, a nozzle portion 5D having a connecting pipe portion 5E connected to the refrigerant pipe 14 from the branch portion 10, a suction portion 5G formed in a tapered shape in the merging portion 5A, and a small diameter mixture connected from the tip of the merging portion 5A It is comprised from the part 5B and the diverging diffuser part 5C connected from the front-end | tip of the mixing part 5B. As shown in FIG. 2B, the ejector 5 flows from the second heat exchanger 7 into the merging portion 5A because the refrigerant reaches a sufficiently low pressure Ps in the suction portion 5G near the outlet of the nozzle portion 5D. The refrigerant can be sucked and can be mixed with the refrigerant ejected from the nozzle portion 5D.

Each component will be individually described below.
The compressor 1 sucks and compresses a refrigerant in a gas state at a low pressure to form a refrigerant in a gas state at a high pressure. Here, as the compressor 1, the operation frequency can be arbitrarily changed by inverter control, that is, the discharge capacity may be variable, or the compressor 1 may be constant speed.

  The condenser 2 condenses the refrigerant in a gas state at a high pressure to a refrigerant in a liquid state at a high pressure by exchanging heat with the external fluid on the heat source side. Here, the external fluid used for heat exchange may be a gas such as air or a liquid such as water.

  The expansion valve 3 expands and decompresses the refrigerant in a liquid state at a high pressure. In Embodiment 1, it is provided in order to adjust the refrigerant flowing into the nozzle portion 5D of the ejector 5 to a saturated liquid state, and it goes without saying that any similar one can be obtained. For example, an electronic expansion valve or a capillary tube may be used.

  Needless to say, the adjustment expansion valve 4 is provided for adjusting the amount of refrigerant flowing into the second evaporator 7 and the evaporation temperature, and can be substituted if there is a similar effect. For example, an electronic expansion valve or a capillary tube may be used.

  The ejector 5 is provided for adjusting the evaporation temperature of the first evaporator 6 and for sucking and increasing the pressure of the refrigerant evaporated by the second evaporator 7, and replaces the one that has the same effect. Needless to say, you can. For example, a variable capacity ejector or a fixed capacity ejector may be used.

  The first evaporator 6 evaporates the low-pressure gas-liquid two-phase refrigerant flowing from the ejector 5 by exchanging heat with air, and returns the refrigerant to the compressor 1 as a low-pressure gas refrigerant. In the first embodiment, the first evaporator 6 is set to have a higher evaporation temperature of the refrigerant than the second evaporator 7 in order to emphasize the sensible heat treatment.

  The second evaporator 7 evaporates the low-pressure gas-liquid two-phase refrigerant flowing from the adjustment expansion valve 4 into the low-pressure gas refrigerant by exchanging heat with air. The refrigerant made into a low-pressure gas state by the second evaporator 7 flows into the mixing unit 5 </ b> A of the ejector 5. The refrigerant that has flowed into the mixing unit 5A merges with the refrigerant from the expansion valve 3, is ejected from the diffuser unit 5B, and flows into the front heat exchanger 6 (in the first embodiment, the refrigerant is sucked and increased in pressure by the ejector 5). Further, in the second evaporator 7 of the first embodiment, the refrigerant evaporation temperature is set lower than that of the first evaporator 6 in order to place importance on the latent heat treatment.

  Needless to say, the refrigerant used in the refrigerant circuit of the air conditioner may be any refrigerant that can be used in the refrigeration cycle. For example, a single refrigerant such as R22, a mixed refrigerant such as R410A, or a natural refrigerant such as CO2 may be used.

  Further, this air conditioner is not composed of only the compressor 1, the condenser 2, the expansion valve 3, the ejector 5, the first evaporator 6, the adjusting expansion valve 4, and the second evaporator 7. For example, a liquid reservoir (accumulator) for protecting the compressor 1 may be provided, or an oil separator for collecting refrigeration machine oil may be provided.

  Next, the operation of the air conditioner according to Embodiment 1 will be described. FIG. 3 shows a Ph diagram illustrating the operation of the air conditioner according to Embodiment 1. 1 to 3, (a) shows the state of the refrigerant flowing into the expansion valve 3, (d) shows the state of the refrigerant that is decompressed by the expansion valve 3 and flows through the branch portion 10, and flows into the ejector 5 from the refrigerant pipe 14. The refrigerant state is (h), the refrigerant state in the mixing section 5B of the ejector 5 is (f), the refrigerant state flowing out from the ejector 5 and flowing into the first evaporator 6 is (g), and the adjusting expansion valve (B) shows the state of the refrigerant flowing out from the refrigerant flow 4 and flowing into the second evaporator 7, (e) shows the state of the refrigerant evaporating in the second evaporator 7 and flows through the bypass pipe 19, and flows out from the first evaporator 6. The state of the refrigerant sucked into the compressor 1 is (c), and the state of the refrigerant discharged from the compressor 1 is (i).

  In the air conditioner according to Embodiment 1, the high-temperature / high-pressure refrigerant in the state (i) discharged from the compressor 1 is cooled by the condenser 2 to be in the low-temperature / high-pressure state (a). The refrigerant in the state (a) is decompressed by the expansion valve 3 to be in the state (d). In order to enhance the effect of the ejector 5, the opening degree of the expansion valve 3 is set in advance so that the refrigerant in the state (d) is in a saturated liquid state. The refrigerant in the state (d) is divided into one that flows into the adjusting expansion valve 4 and one that flows into the ejector 5 at the branching section 10. The refrigerant flowing into the adjustment expansion valve 4 through the bypass pipe 17 is decompressed to be in a gas-liquid two-phase state (state (b)) at a low temperature and low pressure, and is evaporated by the second evaporator 7 to have a low temperature and low pressure. It enters a gas state (state (e)), and flows into the junction 5A of the ejector 5 through the bypass pipe 19 and is sucked. On the other hand, the refrigerant flowing into the nozzle portion 5D of the ejector 5 from the branch portion 10 through the refrigerant pipe 14 is ejected from the nozzle portion 5D and mixed with the refrigerant from the second evaporator 7 to be in the state (f). 1 flows into the evaporator 6. The refrigerant in the state (f) is pressurized by the mixing unit 5B of the ejector 5 to be in the state (g). The refrigerant in the state (g) exchanges heat with room air in the first evaporator 6 and evaporates to become a low-temperature and low-pressure gas state (state (c)), and then is sucked into the compressor 1. As described above, by providing the second evaporator 7 having a low evaporation temperature, it is possible to suppress the decrease in the dehumidification amount and to increase the low pressure side pressure of the refrigerant and return it to the compressor 1. There is no decrease, and energy-saving operation can be realized.

The Ph diagram of FIG. 3 shows an example of the air conditioner according to the first embodiment where the refrigerant pressure increase effect by the ejector 5 is 0.1 kgf / cm 2. (A)-(i) in a figure each represents the state of the refrigerant | coolant which circulates in this refrigerant circuit and changes. The states (a) to (d) are the expansion valve 3, the states (d) to (h) are the nozzle portion 5D of the ejector 5, and the states (h) to (f) to (g) are the mixing of the ejector 5. Part 5A and diffuser part 5C, states (d) to (b) are adjustment expansion valves 4, states (b) to (e) are the second evaporator 7, and states (e) to (f) are ejectors. 5, states (g) to (c) represent the first evaporator 6, and states (c) to (i) represent refrigerant state changes caused by the compressor 1, respectively. The refrigerant circulation rate is assumed to be Gr = 600 kg / h. In order to enhance the boosting effect at the ejector, it is necessary to amplify the acceleration width at the nozzle portion 5D, that is, to increase the enthalpy difference between the state (b) and the state (h). The refrigerant is branched after the pressure is reduced by the expansion valve 3 so as to be in a saturated liquid phase state. For this reason, the appropriate expansion valve 3 is required in the states (a) to (d). Although the state (a) and the state (d) may be the same point, it is not a good idea because the enthalpy difference between the state (b) and the state (e) becomes small. In the first evaporator 6, the evaporation capacity is Qe = 17.8 kW, so that the evaporation capacity in the second evaporator 7 is Qe = 9.0 kW in order to obtain the same evaporation capacity as the conventional one. That is, the circulation amount of the refrigerant flowing from the state (d) to the state (b) requires Gr = 201 kg / h. The circulation amount of the refrigerant flowing from the state (d) to the state (h) is Gr = 399 kg / h. Further, the state (d) to the state (h) and the state (f) to the state (g) are isentropic changes. Since the pressure in the state (c) is the same as the above-described refrigeration cycle operation during the energy saving operation, the air conditioner of the first embodiment can also perform the energy saving operation.

The air diagram of FIG. 4 shows the case where the pressure increase effect of the refrigerant by the ejector 5 is 0.1 kgf / cm 2 in the air conditioner according to the first embodiment. Coordinates A to C to BB indicated by solid lines represent an air diagram by the air conditioner of the first embodiment, and coordinates A to B ′ indicated by broken lines represent an air diagram by a conventional air conditioner. . Coordinates A to C indicate changes in the state of the use side air in the first evaporator 6 on the upstream side, and coordinates C to BB indicate changes in the state of the use side air in the second evaporator 7 on the downstream side. ing. The gradients of coordinates A to C, coordinates C to BB, and coordinates A to B ′ represent SHF (sensible heat ratio) and are determined by the evaporation temperature of the refrigerant. Here, the air volume is V = 90 m 3 / min. In coordinates A to C, the dehumidification amount in the first evaporator 6 is L = 4.43 kg / min, and in coordinates C to BB, the dehumidification amount in the second evaporator 7 is L = 2.62 kg / min. The dehumidifying amount L of 7.06 kg / min is obtained in total of the vessel 6 and the second evaporator 7.

As can be seen from the above, the air conditioner of the first embodiment can dehumidify more than the refrigeration cycle operation during the energy saving operation by the conventional air conditioner described above, and the amount of dehumidification can be reduced while performing the energy saving operation. The decline could be suppressed. In addition, the configuration is simply provided with the adjusting expansion valve 4, the second evaporator 7, and the ejector 5. Moreover, since a hygroscopic device and a hygroscopic material are not required, maintenance load and running cost can be reduced. And since the 1st evaporator 6 and the 2nd evaporator 7 are comprised integrally, it cannot be overemphasized that the evaporator itself can be comprised compactly, and the swing of refrigerant | coolant piping and bypass piping can also be made compact and it looks good.

  Here, the table of FIG. 5 shows the relationship between the refrigerant pressure increase by the ejector 5 and the total evaporation capability and total dehumidification amount of the first evaporator 6 and the second evaporator 7. According to the table of FIG. 5, even when the pressure increase of the refrigerant by the ejector 5 of the first embodiment increases, the evaporation capacity and dehumidification amount by the first evaporator 6 and the evaporation capacity by the second evaporator 7 are both constant. However, the amount of dehumidification by the second evaporator 7 is increasing. As a result, the total evaporation capacity is constant, but the total dehumidification amount is increasing.

  On the other hand, as a comparative form, the second evaporator 7 connected to the adjustment expansion valve 4 is disposed upstream in the ventilation direction (upwind) in the common ventilation path, and the first evaporator 6 connected to the ejector 5 is provided. An experimental example of the refrigerant circuit arranged in the lee is also shown in the table of FIG. According to this comparative form, the dehumidification amount by the second evaporator 7 on the windward increases with the pressure increase by the ejector 5, but the dehumidification amount by the first evaporator 6 on the leeward side decreases. As a result, the total dehumidification amount tends to increase somewhat, but is generally lower than the total dehumidification amount according to the first embodiment. That is, by disposing the first evaporator 6 upstream of the second evaporator 7 in the ventilation direction as in the first embodiment, the total dehumidification amount can be increased without changing the total evaporation capacity.

In the first embodiment, an example in which the first evaporator 6 and the second evaporator 7 are disposed in an integral casing is illustrated. However, the first evaporator 6 and the second evaporator 7 are configured separately. For example, it is also possible to arrange in the air passage 9A of the air passage casing 9 shown in FIG. Even with such a configuration, by disposing the first evaporator 6 upstream of the second evaporator 7 in the ventilation direction, the total dehumidification amount can be increased without changing the total evaporation capacity.
The first heat exchanger and the second heat exchanger having different evaporation temperatures can be used. However, in order to increase the suction pressure of the compressor, some pressure increase mechanism (in the above, an ejector) is required. Become. When the above ejector is used, a combination of an expansion valve and a pump is required.

1 Compressor 2 Condenser 3 Expansion Valve 4 Adjustment Expansion Valve 5 Ejector (Pressure Boosting Mechanism)
5A Junction part 5B Mixing part 5C Diffuser part 5D Nozzle part 5E Connection pipe part 5F Connection pipe part 5G Suction part 6 1st evaporator 7 2nd evaporator 9 Air passage casing 9A Ventilation path 10 Branching parts 11-16 Refrigerant piping 17- 19 Bypass piping 20 Blower W Arrow

Claims (3)

A compressor that compresses and discharges the refrigerant; a condenser that exchanges heat between the refrigerant discharged from the compressor and the heat source side fluid; and an expansion valve that decompresses the refrigerant from the condenser to bring it into a saturated liquid state And a first evaporator that performs sensible heat removal processing on the use side air by heat exchange with the refrigerant from the expansion valve, respectively, are connected in an annular shape through refrigerant piping,
And a pressure increasing mechanism that is arranged in a refrigerant pipe between the expansion valve and the first evaporator, and pressurizes the refrigerant from the expansion valve and sends it to the first evaporator;
A branching section that is provided in a refrigerant pipe between the expansion valve and the pressure increasing mechanism and branches the refrigerant decompressed to a saturated liquid state by the expansion valve ;
A bypass pipe connecting the branch part and the junction part of the booster mechanism;
An expansion valve for adjustment, which is arranged in the bypass pipe and further depressurizes the refrigerant depressurized to the saturated liquid state from the branch part;
A bypass pipe disposed downstream of the adjustment expansion valve in the refrigerant flow direction and performing a heat removal process on the use side air from the first evaporator by exchanging heat with the refrigerant from the adjustment expansion valve. Two evaporators,
With
The refrigerant decompressed to the saturated liquid state by the expansion valve flows into the bypass pipe from the branch part and flows into the refrigerant pipe from the branch part and further from the branch part. An air conditioner characterized in that the enthalpy difference from the state of the refrigerant sent to the pressure increasing mechanism in the saturated liquid state is increased, and the acceleration width of the refrigerant is amplified by the pressure increasing mechanism. The first evaporator and the second evaporator are disposed in a common ventilation path, and the first evaporator is disposed upstream of the second evaporator in the ventilation direction in the ventilation path. The air conditioner according to claim 1, wherein The first evaporator and the second evaporator are integrally formed, and the first evaporator and the second evaporator are so configured that the use-side air passes from the first evaporator to the second evaporator. The air conditioner according to claim 1 or 2, wherein an air passage is formed in the chamber.

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