WO2018154628A1 - Air conditioning device - Google Patents

Abstract

Provided is an air conditioning device comprising: a refrigerant circuit in which a compressor, a heat source-side heat exchanger, an expansion part, and a refrigerant and heat-medium heat exchanger are connected by a refrigerant piping, and through which a refrigerant circulates; and a heat medium circuit in which a pump, the refrigerant and heat-medium heat exchanger, and a load-side heat exchanger that exchanges heat with air in an air conditioning space are connected by a heat medium piping, and through which the heat medium circulates. The air conditioning device further includes: a separation section which is provided outside the air conditioning space, in a portion of the heat medium piping through which the heat medium that has flown out of the refrigerant and heat-medium heat exchanger passes before flowing into the load-side heat exchanger, and which separates the refrigerant from the heat medium; and a discharge section which is connected to the separation section, and which discharges the refrigerant separated by the separation section to the outside of the air conditioning space.

Description

Air conditioner

The present invention relates to an air conditioner including a refrigerant heat medium heat exchanger that exchanges heat between a refrigerant and a heat medium.

Conventionally, there is known an air conditioner in which a refrigerant flowing in a refrigerant circuit and a heat medium flowing in a heat medium circuit are heat-exchanged by a refrigerant heat medium heat exchanger. Patent Document 1 discloses an air conditioner including a primary circuit on the heat source side and a secondary circuit on the indoor side. In Patent Literature 1, heat is exchanged between the refrigerant flowing in the primary circuit and the heat medium flowing in the secondary circuit by the main heat exchanger. Thus, patent document 1 is trying to suppress that a refrigerant | coolant flows into indoor piping by not flowing a refrigerant | coolant into the secondary side circuit of an indoor side.

Japanese Patent Laid-Open No. 2000-130877

Here, in the air conditioner disclosed in Patent Document 1, when the main heat exchanger is built in an outdoor heat source unit or the like, the main heat exchanger may freeze. When the main heat exchanger is punctured due to freezing, the refrigerant flows into the secondary circuit through the main heat exchanger and may flow into the indoor piping.

The present invention has been made in order to solve the above-described problems. Even if the refrigerant flows into the heat medium circuit, the air conditioner suppresses the refrigerant from flowing into the heat medium pipe provided in the room. A device is provided.

An air conditioner according to the present invention includes a refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion unit, and a refrigerant heat medium heat exchanger are connected by a refrigerant pipe, the refrigerant circulates, a pump, and heat between the refrigerant heat mediums. A load side heat exchanger that exchanges heat with air in the air-conditioned space is connected by a heat medium pipe, and a heat medium circuit in which the heat medium circulates. A separation unit that separates the refrigerant and the heat medium is provided outside the air-conditioned space in the heat medium pipe through which the heat medium before flowing into the heat exchanger flows, and is connected to the separation unit and separated by the separation unit A discharge unit that discharges the refrigerant to the outside of the air-conditioned space.

According to the present invention, the refrigerant and the heat medium are separated by the separation unit provided outside the air-conditioned space, and the separated refrigerant is discharged outside the air-conditioned space by the discharge unit. For this reason, even if a refrigerant | coolant flows in into a heat carrier circuit, a refrigerant | coolant is discharged | emitted outside the air-conditioned space via a separation part and a discharge part. Therefore, it is possible to suppress the refrigerant from flowing into the heat medium pipe provided in the room.

It is a circuit diagram which shows the air conditioning apparatus 1 which concerns on Embodiment 1 of this invention. It is a schematic diagram which shows the isolation | separation part 4 in Embodiment 1 of this invention. It is a graph which shows the relationship between the bubble diameter and bubble rising speed in Embodiment 1 of this invention. It is a graph which shows the relationship between the water flow rate in Embodiment 1 of this invention, and discharge | emission amount / inflow amount. It is a schematic diagram which shows the isolation | separation part 4a in the 1st modification of Embodiment 1 of this invention. It is a schematic diagram which shows the isolation | separation part 4b in the 2nd modification of Embodiment 1 of this invention. It is a schematic diagram which shows the isolation | separation part 4c in the 3rd modification of Embodiment 1 of this invention. It is a schematic diagram which shows the separation part 4d in the 4th modification of Embodiment 1 of this invention. It is a circuit diagram which shows the air conditioning apparatus 100 which concerns on Embodiment 2 of this invention. It is a circuit diagram which shows the air conditioning apparatus 100a which concerns on the 1st modification of Embodiment 2 of this invention. It is a circuit diagram which shows the air conditioning apparatus 100b which concerns on the 2nd modification of Embodiment 2 of this invention. It is a circuit diagram which shows the air conditioning apparatus 200 which concerns on Embodiment 3 of this invention. It is a circuit diagram which shows the air conditioning apparatus 300 which concerns on Embodiment 4 of this invention. It is a circuit diagram which shows the air conditioning apparatus 400 which concerns on Embodiment 5 of this invention. It is a graph which shows the relationship between the pressure of the refrigerant | coolant in Embodiment 5 of this invention, and the saturation temperature of a refrigerant | coolant. It is a circuit diagram which shows the air conditioning apparatus 600 which concerns on Embodiment 7 of this invention. It is a circuit diagram which shows the air conditioning apparatus 700 which concerns on Embodiment 8 of this invention. It is a circuit diagram which shows the air conditioning apparatus 800 which concerns on Embodiment 9 of this invention. It is a circuit diagram which shows the air conditioning apparatus 900 which concerns on Embodiment 10 of this invention. It is a circuit diagram which shows the air conditioning apparatus 1000 which concerns on Embodiment 11 of this invention. It is a circuit diagram which shows the air conditioning apparatus 1100 which concerns on Embodiment 12 of this invention. It is a circuit diagram which shows the air conditioning apparatus 1200 which concerns on Embodiment 13 of this invention. It is a schematic diagram which shows the subseparation part 13 in Embodiment 14 of this invention. It is a schematic diagram which shows the subseparation part 13a in the modification of Embodiment 14 of this invention.

Embodiment 1 FIG.
Hereinafter, embodiments of an air-conditioning apparatus according to the present invention will be described with reference to the drawings. FIG. 1 is a circuit diagram showing an air conditioner 1 according to Embodiment 1 of the present invention. The air conditioner 1 will be described with reference to FIG. As shown in FIG. 1, the air conditioner 1 includes a refrigerant circuit 2, a heat medium circuit 3, a separation unit 4, and a discharge unit 5.

(Refrigerant circuit 2)
The refrigerant circuit 2 is a circuit in which the refrigerant is circulated by connecting the compressor 22, the flow path switching device 23, the heat source side heat exchanger 24, the expansion unit 25, and the refrigerant heat exchanger related to heat medium 26 through the refrigerant pipe 21. The compressor 22, the flow path switching device 23, the heat source side heat exchanger 24, the expansion unit 25, and the refrigerant heat medium heat exchanger 26 are built in the heat source device 20. Refrigerant flowing through the refrigerant circuit 2 may be R410A or R407C, R1234yf is slightly combustible refrigerant, may be R1234ze, R32 or R290, or a CO ₂ a natural refrigerant. In the first embodiment, the case where the heat source device 20 is an air-cooled model installed outdoors is illustrated. The air-cooled model is a model in which the heat source side heat exchanger 24 exchanges heat between the refrigerant and the outdoor air. The heat source unit 20 may be a water-cooled model installed indoors. The water-cooled model refers to a model in which the heat source side heat exchanger 24 exchanges heat between the refrigerant and water.

(Compressor 22, flow path switching device 23)
The compressor 22 is a device that draws in a low-temperature and low-pressure refrigerant, compresses the drawn refrigerant, and discharges it into a high-temperature and high-pressure refrigerant. The compressor 22 is an inverter compressor capable of controlling the capacity, for example. The flow path switching device 23 is a device that switches the direction in which the refrigerant flows in the refrigerant circuit 2, and is, for example, a four-way valve. The flow path switching device 23 switches whether the refrigerant discharged from the compressor 22 flows into the refrigerant heat medium heat exchanger 26 (solid line in FIG. 1) or the heat source side heat exchanger 24 (broken line in FIG. 1). Thus, both the heating operation and the cooling operation are performed. When only one of the heating operation and the cooling operation is performed, the flow path switching device 23 may be omitted.

(Heat source side heat exchanger 24, expansion part 25)
The heat source side heat exchanger 24 is connected between the flow path switching device 23 and the expansion unit 25, and is a device that exchanges heat between outdoor air and a refrigerant, for example. The heat source side heat exchanger 24 acts as an evaporator during heating operation, and acts as a condenser during cooling operation. The heat source unit 20 may be provided with a heat source side blower that sends outdoor air to the heat source side heat exchanger 24. The expansion unit 25 is connected between the heat source side heat exchanger 24 and the refrigerant heat medium heat exchanger 26, and is a pressure reducing valve or an expansion valve that expands by depressurizing the refrigerant. The expansion part 25 is an electronic expansion valve whose opening degree is adjusted, for example.

(Refrigerant heat medium heat exchanger 26)
The refrigerant heat medium heat exchanger 26 is connected between the expansion unit 25 and the flow path switching device 23, and exchanges heat between the refrigerant flowing in the refrigerant circuit 2 and the heat medium flowing in the heat medium circuit 3. Equipment. In the inter-refrigerant heat medium heat exchanger 26, the refrigerant flow and the heat medium flow are, for example, counterflows.

(Heat medium circuit 3)
The heat medium circuit 3 is a circuit in which the pump 32, the refrigerant heat medium heat exchanger 26, and the load side heat exchanger 33 are connected by the heat medium pipe 31, and the heat medium circulates. The heat medium flowing through the heat medium circuit 3 can be water or brine. The heat medium circuit 3 is provided with an air vent valve 34.

(Pump 32, load side heat exchanger 33, air vent valve 34)
The pump 32 is a device that is provided on the upstream side of the heat exchanger 26 between the refrigerant and heat medium outside and conveys the heat medium. The load-side heat exchanger 33 is a device that is provided on the downstream side of the refrigerant heat medium heat exchanger 26 in the room and exchanges heat between, for example, room air and the heat medium. The load side heat exchanger 33 acts as a condenser during heating operation, and acts as an evaporator during cooling operation. The load-side heat exchanger 33 is built in the air conditioning appliance 30, and the heating operation or the cooling operation of the air conditioning appliance 30 is performed by the heat exchange of the load side heat exchanger 33. The air vent valve 34 is provided on the downstream side of the load-side heat exchanger 33 and is a valve that vents air mixed in the heat medium flowing in the heat medium circuit 3. Here, the indoor means a residential space of a house or a public place. The room in the first embodiment indicates an air-conditioned space.

(Separation part 4)
The separation unit 4 is provided outside the air-conditioned space in the heat medium pipe 31 through which the heat medium flows out from the refrigerant heat medium heat exchanger 26 and flows into the load-side heat exchanger 33, and the refrigerant and heat Separate media. In the first embodiment, the separation unit 4 is a member that is provided outside the room, has a connection port 41, a discharge port 42, and an outflow port 43, and separates gas and liquid. The connection port 41 is an opening connected to the downstream side of the refrigerant heat medium heat exchanger 26 in the heat medium circuit 3. The discharge port 42 is an opening that is formed, for example, in the upper part of the separation unit 4 and discharges the gas in the separation unit 4. The outflow port 43 is an opening that is connected to the upstream side of the load-side heat exchanger 33 in the heat medium circuit 3 and from which liquid flows out. The separation unit 4 is a member that separates the fluid flowing out from the refrigerant heat exchanger 26 into gas and liquid, discharges the gas from the discharge port 42, and causes the liquid to flow out from the outflow port 43.

FIG. 2 is a schematic diagram showing the separation unit 4 according to Embodiment 1 of the present invention. As shown in FIG. 2, the separation unit 4 has an extending part 44, a discharge part 45, and an outflow part 46. The extending part 44 is a pipe that extends upward from the connection port 41 connected to the heat medium pipe 31 and extends laterally from the upper end. The outflow portion 46 is a pipe that extends downward from the extending portion 44 and is connected to the outflow port 43. The discharge part 45 is a pipe provided above the outflow part 46 and connected to the discharge port 42.

The fluid flowing in the heat medium pipe 31 flows in from the connection port 41 and rises in the extending portion 44. During this time, when gas is mixed in the fluid, small bubbles gather and become large bubbles. As described above, the fluid flowing through the heat medium pipe 31 can be prevented from flowing out of the separation unit 4 as it is by being temporarily dammed by the extending part 44. In this way, the gas and the liquid are separated by the separation unit 4. As described above, the separation unit 4 according to the first embodiment is composed of a composite pipe that traps gas.

In addition, the separation unit 4 has a function of collecting the gas upward by increasing the force by which the fluid rises by buoyancy rather than the force by which the fluid sinks downward by gravity due to the decrease in the flow velocity of the fluid. . Here, it is assumed that the refrigerant heat exchanger related to heat medium 26 is punctured due to freezing or the like. When the refrigerant heat exchanger related to heat medium 26 is punctured, the refrigerant may enter the heat medium flow path in the refrigerant heat exchanger related to heat medium 26 and flow into the heat medium circuit 3. In this case, the refrigerant is vaporized to some extent by the heat medium flowing in the heat medium circuit 3. This is generally due to the fact that the boiling point of the refrigerant is lower than the boiling point of the heat medium.

Here, the flow path cross-sectional area of the discharge part 45 and the outflow part 46 of the separation part 4 is larger than the flow path cross-sectional area of the heat medium pipe 31. In the first embodiment, the heat medium pipe 31 and the flow path switching unit are both circular pipes. As shown in FIG. 2, when the pipe diameter of the heat medium pipe 31 is d ₁ , the pipe diameters of the discharge section 45 and the outflow section 46 of the separation section 4 are d ₂ , and the circumference is π, the heat medium pipe 31. the flow path cross-sectional area is ^{_{π (d 1/2) 2}} , flow path cross-sectional area of the discharge portion 45 and the outlet portion 46 is ^{_{π (d 2/2) 2}} , π (d 2/2) 2> π _(d ^1/2) 2 of the relationship is established. As described above, the flow velocity of the fluid flowing through the heat medium pipe 31 is reduced by flowing into the discharge portion 45 and the outflow portion 46 of the separation portion 4 where the flow path cross-sectional area is widened.

FIG. 3 is a graph showing the relationship between the bubble diameter and the bubble rising speed in the first embodiment of the present invention. Next, the relationship between the bubble diameter and the bubble rising speed will be described. In FIG. 3, the horizontal axis is the bubble diameter [mm], and the vertical axis is the bubble rising speed [mm / s] in water. The solid line indicates the bubble density 1.25 [kg / m ³ ], the two-dot chain line indicates the bubble density 50.0 [kg / m ³ ], and the broken line indicates the bubble density 100.0 [kg / m ³ ]. Show. Here, the lower the bubble density, the more gasified, and the higher the bubble density, the more liquefied. The bubble density of the gas is about 1.25 to 1.50 [kg / m ³ ], which corresponds to the solid line in FIG. As shown in FIG. 3, regardless of the bubble density, the bubble rising speed in water increases as the bubble diameter increases. Moreover, the bubble rising speed is higher as the bubble density is lower.

In general, the flow rate of fluid flowing through a pipe having a nominal diameter of 50 [A] (outer diameter of about 60.5 [mm]) is 16 [m ³ / h], and the flow velocity is about 2000 [mm / s]. Here, the diameter of the refrigerant on the bubble generated from the crack portion of the refrigerant heat exchanger 26 is observed to be about 1.5 [mm] or more. Therefore, when the heat medium pipe 31 having a nominal diameter of 50 [A] is used, a pipe having a nominal diameter of 80 [A] (outer diameter of 89.1 [mm]) or more is connected to the discharge section 45 and the outflow section of the separation section 4. By using it as 46, the flow rate becomes 1000 [mm / s] or less. As shown in FIG. 3, when the flow rate is 1000 [mm / s], the bubble diameter is about 1.4 [mm]. That is, a bubble having a bubble diameter of about 1.4 [mm] or more has a higher force that rises by buoyancy than the force by which the fluid sinks downward due to gravity. Therefore, almost all of the bubble-like refrigerant in the separation unit 4 can be collected upward. In the first embodiment, the flow path cross-sectional area of the separation unit 4 may not be larger than the flow path cross-sectional area of the heat medium pipe 31.

FIG. 4 is a graph showing the relationship between the water flow rate and the discharge / inflow in the first embodiment of the present invention. Next, the relationship between the flow rate of water and the ratio obtained by dividing the discharge amount from the discharge unit 5 by the inflow amount will be described. In FIG. 4, the horizontal axis represents water flow velocity [mm / s], and the vertical axis represents discharge / inflow [%]. As shown in FIG. 4, when the water flow rate is 1500 mm / s, the discharge / inflow is about 75%, and the discharge is sufficient. Thus, since the separation part 4 has a flow path cross-sectional area in which the internal water flow velocity is 1500 mm / s or less, it is possible to efficiently separate the gas and the liquid. Thereby, the gas which flowed in can be efficiently discharged | emitted from the discharge part 5. FIG.

(Discharge unit 5)
As shown in FIG. 1, the discharge unit 5 is connected to an outlet 43 of the separation unit 4 and is formed with a discharge port 51 that discharges the refrigerant separated by the separation unit 4 to the outside of the air-conditioned space. The discharge part 5 is comprised, for example from the gas vent valve or the gas relief valve. In the first embodiment, the separation unit 4 and the discharge unit 5 are provided outside the heat source unit 20. For this reason, the existing heat source machine 20 can be used. Moreover, since the separation part 4 and the discharge part 5 can be arrange | positioned in the position different from the heat-source equipment 20, it can also be arrange | positioned, for example in the high place as possible. In this case, the effect that the discharge part 5 discharges gas increases.

(Operation mode)
Next, the operation mode of the air conditioner 1 will be described. The air conditioner 1 has a heating operation mode and a cooling operation mode as operation modes. The heating operation mode and the cooling operation mode will be described with reference to FIG.

(Heating operation)
First, the heating operation will be described. In the heating operation, the discharge side of the compressor 22 and the refrigerant heat medium heat exchanger 26 are connected by the flow path switching device 23, and the suction side of the compressor 22 and the heat source side heat exchanger 24 are connected. (Solid line in FIG. 1). First, the flow of the refrigerant in the refrigerant circuit 2 will be described. In the heating operation, the refrigerant sucked into the compressor 22 is compressed by the compressor 22 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gas refrigerant discharged from the compressor 22 passes through the flow path switching device 23 and flows into the refrigerant heat exchanger related to heat medium 26 that functions as a condenser. The refrigerant flowing into the inter-refrigerant heat medium heat exchanger 26 is heat-exchanged with the heat medium to be condensed and liquefied. At this time, the heat medium is heated. The condensed refrigerant in the liquid state is expanded and depressurized in the expansion section 25 to become a low-temperature low-pressure gas-liquid two-phase refrigerant. Then, the gas-liquid two-phase refrigerant flows into the heat source side heat exchanger 24 acting as an evaporator, and in the heat source side heat exchanger 24, heat is exchanged with, for example, outdoor air to evaporate. The evaporated refrigerant in the low-temperature and low-pressure gas state passes through the flow path switching device 23 and is sucked into the compressor 22.

Next, the flow of the heat medium in the heat medium circuit 3 will be described. The heat medium conveyed by the pump 32 flows into the refrigerant heat medium heat exchanger 26. The heat medium flowing into the refrigerant heat medium heat exchanger 26 is heat-exchanged with the refrigerant and heated. The heated heat medium passes through the separation unit 4 and flows into a load-side heat exchanger 33 provided in the room. In the load-side heat exchanger 33, for example, heat is exchanged with room air to be cooled. Is done. At this time, room air is heated and the room is heated. The cooled heat medium is then sucked into the pump 32.

(Cooling operation)
Next, the cooling operation will be described. In the cooling operation, the discharge side of the compressor 22 and the heat source side heat exchanger 24 are connected by the flow path switching device 23, and the suction side of the compressor 22 and the refrigerant heat medium heat exchanger 26 are connected. (Dashed line in FIG. 1). First, the flow of the refrigerant in the refrigerant circuit 2 will be described. In the cooling operation, the refrigerant sucked into the compressor 22 is compressed by the compressor 22 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure gas refrigerant discharged from the compressor 22 passes through the flow path switching device 23 and flows into the heat source side heat exchanger 24 acting as a condenser. The refrigerant that has flowed into the heat source side heat exchanger 24 is heat-exchanged with, for example, outdoor air to be condensed and liquefied. The condensed refrigerant in the liquid state is expanded and depressurized in the expansion section 25 to become a low-temperature low-pressure gas-liquid two-phase refrigerant. The refrigerant in the gas-liquid two-phase state flows into the refrigerant heat medium heat exchanger 26 acting as an evaporator, and heat is exchanged with the heat medium in the refrigerant heat medium heat exchanger 26 to evaporate the gas. Turn into. At this time, the heat medium is cooled. The evaporated refrigerant in the low-temperature and low-pressure gas state passes through the flow path switching device 23 and is sucked into the compressor 22.

Next, the flow of the heat medium in the heat medium circuit 3 will be described. The heat medium conveyed by the pump 32 flows into the refrigerant heat medium heat exchanger 26. The heat medium flowing into the inter-refrigerant heat medium heat exchanger 26 is cooled by exchanging heat with the refrigerant. The cooled heat medium passes through the separation unit 4 and flows into a load-side heat exchanger 33 provided in the room. In the load-side heat exchanger 33, heat is exchanged with, for example, room air and heated. Is done. At this time, the room air is cooled and the room is cooled. The heated heat medium is then sucked into the pump 32.

(Operation when refrigerant flows in)
Next, the operation when the refrigerant flows into the heat medium circuit 3 will be described. Here, it is assumed that the refrigerant heat exchanger 26 is punctured due to freezing or the like. When the refrigerant heat exchanger related to heat medium 26 is punctured, the refrigerant may enter the heat medium flow path in the refrigerant heat exchanger related to heat medium 26 and flow into the heat medium circuit 3.

The refrigerant that has flowed into the heat medium circuit 3 passes from the refrigerant heat medium heat exchanger 26 to the separation unit 4 through the heat medium pipe 31. The refrigerant flows in from the connection port 41 of the separation part 4 and rises in the extension part 44. At this time, the refrigerant sinking below the extending portion 44 rises forcibly with the flow of the heat medium. During this time, small bubble refrigerants gather to form large bubbles. As described above, the refrigerant flowing through the heat medium pipe 31 is temporarily blocked by the extending portion 44, and therefore, it is possible to suppress the refrigerant from flowing out of the separation unit 4 together with the heat medium. The refrigerant that has risen up the extending portion 44 flows into the discharge portion 45 and the outflow portion 46 having a flow passage cross-sectional area larger than the flow passage cross-sectional area of the heat medium pipe 31. At this time, when the flow rate of the refrigerant decreases, the force that floats on the discharge part 45 side is greater than the force that sinks on the outflow part 46 side together with the heat medium, and the refrigerant rises on the discharge part 45 side.

Moreover, since the flow of the heat medium containing the refrigerant stagnates when the cross-sectional area of the flow path widens, the refrigerant can be collected in the portion where the flow is stagnant. Thereby, small bubble-like refrigerants gather to form large bubbles. Accordingly, the refrigerant further rises toward the discharge portion 45 side. The refrigerant that has reached the discharge part 45 reaches the discharge part 5 through the discharge port 42. And a refrigerant | coolant is discharged | emitted from the discharge part 5 outdoors. The heat medium not mixed with the refrigerant descends the outflow portion 46 and flows out from the outlet 43 to the heat medium pipe 31. Therefore, the refrigerant does not flow into the heat medium pipe 31 provided in the room.

According to the first embodiment, the refrigerant and the heat medium are separated by the separation unit 4 provided outside the air-conditioned space, and the separated refrigerant is discharged by the discharge unit 5 to the outside of the air-conditioned space. For this reason, even if the refrigerant flows into the heat medium circuit 3, the refrigerant is discharged to the outside of the air-conditioned space through the separation unit 4 and the discharge unit 5. Accordingly, the refrigerant is prevented from flowing into the heat medium pipe 31 provided in the room.

Further, the flow path cross-sectional area of the separation unit 4 is larger than the flow path cross-sectional area of the heat medium pipe 31. For this reason, the separation unit 4 can reduce the flow velocity of the fluid and increase the floating force more than the force that the fluid sinks. Accordingly, the refrigerant can be further discharged. Further, the separation part 4 is positioned below the discharge part 45, an extension part 44 extending upward from the connection port 41, a discharge part 45 extending upward from the extension part 44 and connected to the discharge port 42, And an outflow part 46 that extends downward from the extension part 44 and is connected to the outlet 43. Thereby, the refrigerant | coolant sinking under the extension part 44 forcibly raises with the flow of a heat carrier. During this time, small bubble refrigerants gather to form large bubbles. As described above, the refrigerant flowing through the heat medium pipe 31 is once blocked by the extending portion 44, so that it can be prevented from flowing out from the separation portion 4 as it is, and the refrigerant can be easily collected. . Further, when the refrigerant is a slightly flammable refrigerant or a flammable refrigerant, safety is further improved by preventing the refrigerant from flowing into the heat medium pipe 31 provided in the room.

(First modification)
FIG. 5 is a schematic diagram showing the separation unit 4a in the first modification of the first embodiment of the present invention. The first modification is different from the first embodiment in the structure of the separation portion 4a. As shown in FIG. 5, the separation portion 4 a of the first modification is a single pipe having a flow path cross-sectional area larger than that of the heat medium pipe 31. _{D 1} a tube diameter of the heat medium pipe 31, the pipe diameter of the separation portion 4a _{d 3,} the circular constant and [pi, the flow path cross-sectional area of the heat medium pipe 31 is ^{_{π (d 1/2) 2}} , the channel cross-sectional area of the discharge portion 45 and the outlet portion 46 is ^{_{π (d 3/2) 2}} , π (d 3/2) 2> π (d 1/2) 2 relation holds. As described above, the flow velocity of the fluid flowing through the heat medium pipe 31 is reduced in the same manner as in the first embodiment by flowing into the separation portion 4a in which the flow path cross-sectional area is widened. Moreover, the connection port 41 of the separation part 4a is formed in the position beyond the outflow port 43 in the height direction. In the first modification, the outlet 43 is formed at the bottom of the separation part 4a.

In the first modification, when the refrigerant flows into the heat medium circuit 3, the refrigerant passes from the refrigerant heat medium heat exchanger 26 through the heat medium pipe 31 to the separation unit 4a. At this time, the refrigerant flows into the separation portion 4 a having a flow path cross-sectional area larger than that of the heat medium pipe 31. For this reason, when the flow rate of the refrigerant decreases, the force that floats on the discharge unit 45 side is greater than the force that sinks on the outflow unit 46 side, and the refrigerant rises toward the upper discharge port 42. The rising refrigerant reaches the discharge part 5 through the discharge port 42. And a refrigerant | coolant is discharged | emitted from the discharge part 5 outdoors. In addition, the heat medium in which the refrigerant is not mixed passes through the separation unit 4 a and flows out from the outlet 43 to the heat medium pipe 31. Accordingly, the refrigerant is prevented from flowing into the heat medium pipe 31 provided in the room.

Moreover, the connection port 41 of the separation part 4a is formed at a position higher than the outflow port 43 in the height direction. For this reason, it is not necessary to prevent the heat medium from smoothly flowing in the separation portion 4a. In addition, the separation part 4a is good also as a cylindrical container instead of piping. Piping has higher availability than containers and can reduce costs, but can be appropriately changed to containers. Thus, since the separation part 4a can be produced simply by connecting a pipe or a cylindrical container to the heat medium pipe 31, productivity and availability are easy.

(Second modification)
FIG. 6 is a schematic diagram showing a separation unit 4b in the second modification of the first embodiment of the present invention. The second modification differs from the first embodiment in the structure of the separation part 4b. As shown in FIG. 6, in the second modification, the outlet 43 is formed on the side surface of the separation portion 4b, and the connection port 41 and the outlet 43 are opposed to each other. Thereby, it is not necessary to prevent the heat medium from flowing smoothly in the separation part 4b. In the second modified example, as in the first modified example, the separation portion 4 b is a single pipe having a flow path cross-sectional area larger than the flow path cross-sectional area of the heat medium pipe 31. Thereby, the flow velocity of the fluid flowing through the heat medium pipe 31 is reduced in the same manner as in the first modification by flowing into the separation portion 4b where the flow path cross-sectional area is widened.

(Third Modification)
FIG. 7 is a schematic diagram showing a separation portion 4c in the third modification of the first embodiment of the present invention. The third modification is different from the first embodiment in the structure of the separation portion 4c. As shown in FIG. 7, in the separation unit 4 c of the third modification example, a pipe constituting the separation unit 4 c extends downward from the separation unit 4 c of the second modification example. Thereby, the scale which generate | occur | produces from the heat medium which flows into the heat-medium piping 31 can be stored in the part extended below. In the third modified example, as in the first modified example, the separation portion 4 c is a single pipe having a flow path cross-sectional area larger than the flow path cross-sectional area of the heat medium pipe 31. Thereby, the flow velocity of the fluid flowing through the heat medium pipe 31 is reduced in the same manner as in the first modification by flowing into the separation portion 4c where the flow path cross-sectional area is widened.

(Fourth modification)
FIG. 8 is a schematic diagram showing a separation unit 4d in a fourth modification of the first embodiment of the present invention. The fourth modification is different from the first embodiment in the structure of the separation part 4d. As shown in FIG. 8, in the separation part 4d of the fourth modified example, the lower end 41a of the connection port 41 is formed at a position higher than the upper end 43a of the outflow port 43 in the height direction. As a result, the heat medium flowing into the separation part 4d from the connection port 41 descends until reaching the outlet 43, so that the heat medium can flow more smoothly in the separation part 4d. In the fourth modified example, as in the first modified example, the separation portion 4d is a single pipe having a flow path cross-sectional area larger than the flow path cross-sectional area of the heat medium pipe 31. Thereby, the flow velocity of the fluid flowing through the heat medium pipe 31 is reduced in the same manner as in the first modification by flowing into the separation portion 4d where the flow path cross-sectional area is widened.

Embodiment 2. FIG.
FIG. 9 is a circuit diagram showing an air conditioner 100 according to Embodiment 2 of the present invention. The second embodiment is different from the first embodiment in that an outlet side valve 7 and an inlet side valve 8 are provided. In the second embodiment, the same parts as those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. The description will focus on differences from the first embodiment.

As shown in FIG. 9, the heat medium circuit 3 is provided with an outlet side valve 7 and an inlet side valve 8. The outlet side valve 7 is a valve that is provided on the downstream side that is the outlet side of the separation unit 4 outside the air-conditioned space and adjusts the flow rate of the heat medium. The outlet side valve 7 may be a valve whose opening degree is adjustable or a valve whose opening degree is fixed. The inlet side valve 8 is a valve that is provided on the upstream side of the separation unit 4, for example, on the downstream side of the pump 32, outside the air-conditioned space, and adjusts the flow rate of the heat medium. The inlet side valve 8 may be a valve whose opening degree is adjustable, a valve whose opening degree is fixed, or a check valve which prevents backflow. One of the outlet side valve 7 and the inlet side valve 8 may be provided. In this case, the refrigerant inflow suppressing effect is higher when only the outlet side valve 7 is installed than when only the inlet side valve 8 is installed.

The outlet side valve 7 and the inlet side valve 8 are closed when the refrigerant flows into the heat medium circuit 3. When the refrigerant flows into the heat medium circuit 3, the refrigerant passes from the refrigerant heat medium heat exchanger 26 to the separation unit 4 through the heat medium pipe 31. At this time, even if the refrigerant flows into the heat medium pipe 31 from the separation unit 4, the outlet side valve 7 is closed, so that it does not advance beyond the outlet side valve 7. For this reason, it can suppress reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. In addition, when the refrigerant flows into the heat medium circuit 3, the refrigerant may flow backward from the refrigerant heat medium heat exchanger 26. However, since the inlet side valve 8 is closed, it does not advance beyond the inlet side valve 8. For this reason, it can suppress more reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. As described above, in the second embodiment, when the refrigerant flows in, the heat medium circuit 3 is separated into the indoor side and the outdoor side by the outlet side valve 7 and the inlet side valve 8. It can suppress flowing into the heat medium piping 31 provided indoors through the room. The configuration for detecting the refrigerant flowing into the heat medium circuit 3 will be described in the fourth embodiment.

(First modification)
FIG. 10 is a circuit diagram showing an air conditioner 100a according to a first modification of the second embodiment of the present invention. In the first modification, the installation location of the heat source device 20 is different from that of the second embodiment. As shown in FIG. 10, the heat source device 20 of the first modification is installed below the room. For example, the case where the heat source unit 20 is provided below the floor rather than indoors is assumed. When the refrigerant flows into the heat medium circuit 3, the refrigerant may rise to the upper indoor side due to buoyancy. When the refrigerant flows into the heat medium circuit 3, even if the pump 32 is stopped, there is a possibility that the refrigerant rises to the upper indoor side because there is buoyancy. However, since the outlet side valve 7 is closed, it does not advance beyond the outlet side valve 7. For this reason, it can suppress reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. Even if the refrigerant flows backward from the refrigerant heat exchanger 26, the inlet side valve 8 is closed, and therefore the refrigerant does not advance beyond the inlet side valve 8. For this reason, it can suppress more reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. Thus, by providing the outlet side valve 7 or the inlet side valve 8, even if the heat source unit 20 is installed below the room, the refrigerant is prevented from flowing into the heat medium pipe 31 provided in the room. be able to.

(Second modification)
FIG. 11 is a circuit diagram showing an air conditioner 100b according to a second modification of the second embodiment of the present invention. The second modified example is different from the second embodiment in that a plurality of air conditioning appliances 30 are connected. As shown in FIG. 11, each of the plurality of air conditioners 30 has a load-side heat exchanger 33, and is connected in parallel in the heat medium circuit 3. In this case, the outlet side valve 7 and the inlet side valve 8 are provided in the heat medium pipe 31 immediately before the heat medium pipe 31 provided with each load side heat exchanger 33 is branched. Even when a plurality of air conditioners 30 are connected as in the second modification, the refrigerant flows into the heat medium pipe 31 provided indoors by providing the outlet side valve 7 or the inlet side valve 8. Can be suppressed.

Embodiment 3 FIG.
FIG. 12 is a circuit diagram showing an air conditioner 200 according to Embodiment 3 of the present invention. In the third embodiment, the installation position of the pump 32 is different from that of the second embodiment. In the third embodiment, the same parts as those in the first or second embodiment are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first and second embodiments.

As shown in FIG. 12, the pump 32 is provided on the downstream side of the refrigerant heat exchanger related to heat medium 26. In the third embodiment, when the refrigerant flows into the heat medium circuit 3, the refrigerant that has passed through the heat medium pipe 31 from the refrigerant heat exchanger 26 is immediately sucked into the pump 32 without passing through the room. Flows into the side. When the refrigerant stays on the suction side of the pump 32, the pump 32 is idle. When the pump 32 is idling, the flow of the heat medium stops or slows down. For this reason, the flow rate of the refrigerant contained in the heat medium also decreases. Further, the liquid refrigerant is easily vaporized due to the decrease in the pressure of the fluid due to the suction of the pump 32. For this reason, the floating force can be made larger than the force by which the refrigerant sinks. Therefore, the refrigerant discharge effect at the separation unit 4 and the discharge unit 5 that flows after passing through the pump 32 is enhanced. As described above, in Embodiment 3, the pump 32 is provided on the downstream side of the refrigerant heat exchanger 26 to cause the pump 32 to run idly and stop the flow of the heat medium. Accordingly, it is possible to further suppress the refrigerant from flowing into the heat medium pipe 31 provided in the room.

Embodiment 4 FIG.
FIG. 13 is a circuit diagram showing an air conditioner 300 according to Embodiment 4 of the present invention. The fourth embodiment is different from the second embodiment in that the refrigerant detection unit 6 is provided. In the fourth embodiment, the same parts as those in the first to third embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on the differences from the first to third embodiments.

As shown in FIG. 13, the air conditioning apparatus 300 includes a refrigerant detection unit 6 that detects that the refrigerant has flowed into the heat medium circuit 3. And the refrigerant | coolant detection part 6 is provided in the discharge port 51 of the discharge part 5, and has the discharge | emission refrigerant | coolant detection part 6a which detects the refrigerant | coolant discharged | emitted from the discharge port 51. FIG. In the fourth embodiment, the refrigerant discharged from the discharge port 51 is directly detected by the discharged refrigerant detector 6a. For this reason, it can be immediately recognized that the refrigerant has flowed into the heat medium circuit 3. The control when the discharged refrigerant detection unit 6a detects the inflow of the refrigerant will be described in the tenth embodiment.

Embodiment 5 FIG.
FIG. 14 is a circuit diagram showing an air conditioner 400 according to Embodiment 5 of the present invention. The fifth embodiment is different from the fourth embodiment in that a heating unit 9 is provided. In the fifth embodiment, the same parts as those in the first to fourth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on the differences from the first to fourth embodiments.

As shown in FIG. 14, the heating unit 9 is provided in the separation unit 4 and heats the liquid in the separation unit 4. The heating unit 9 is, for example, a heater. When the refrigerant flows into the heat medium circuit 3, the refrigerant may circulate in the heat medium circuit 3 in a liquid state depending on the pressure and temperature of the heat medium flowing through the heat medium circuit 3. At this time, the liquid refrigerant flowing into the separation unit 4 is heated by the heating unit 9. As a result, the liquid refrigerant is vaporized and discharged to the outside by the separation unit 4 and the discharge unit 5. Also, during maintenance such as trial operation or periodic inspection, when the operation of the heat source device 20 is stopped and the temperature of the heat medium is decreasing, the refrigerant flowing into the heat medium circuit 3 stays in the heat medium circuit 3 in a liquid state. To do. Also in this case, the liquid refrigerant flowing into the separation unit 4 is heated by the heating unit 9. As a result, the liquid refrigerant is vaporized and discharged to the outside by the separation unit 4 and the discharge unit 5.

Furthermore, when the refrigerant flows into the heat medium circuit 3, there is a possibility that the refrigerant in the heat source unit 20 runs short and the heat source unit 20 becomes inoperable. In this case, since the heat medium and the refrigerant cannot be heated using the heat source device 20, the refrigerant is cooled and condensed by the outside air or the like. The condensed liquid refrigerant stays in the heat medium circuit 3. On the other hand, in this Embodiment 5, since the temperature of a heat medium and a refrigerant | coolant can be raised with a heater instead of the heat source apparatus 20, it can prevent that a refrigerant | coolant condenses and can vaporize a refrigerant | coolant further.

FIG. 15 is a graph showing the relationship between the refrigerant pressure and the refrigerant saturation temperature in the fifth embodiment of the present invention. Next, the easiness of vaporization for each refrigerant will be described. In FIG. 15, the horizontal axis represents pressure [MPaA] and the vertical axis represents saturation temperature [° C.]. In addition, a solid line indicates R32, a two-dot chain line indicates R1234yf, and a broken line indicates R1234ze. In FIG. 14, the area below each line is a liquid state area, and the area above each line is a gas state area. As shown in FIG. 14, R1234yf and R1234ze are less likely to vaporize than R32. For this reason, this Embodiment 5 has a remarkable effect in the air conditioning apparatus 400 using R1234yf and R1234ze which are hard to vaporize.

Embodiment 6 FIG.
The sixth embodiment is different from the first to fifth embodiments in that the separation unit 4 and the discharge unit 5 are built in the heat source unit 20. In the sixth embodiment, the same parts as those in the first to fifth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first to fifth embodiments.

Since the separation unit 4 and the discharge unit 5 are built in the heat source unit 20, the structure of the heat medium circuit 3 can be simplified. Here, when the heat source side air blower used for heat dissipation or heat exchange is provided inside the heat source device 20, the heat source side heat exchanger 24 blows air, whereby the refrigerant in the separation unit 4 can be agitated. . Thereby, since the density | concentration of a refrigerant | coolant can be reduced, safety | security improves.

Embodiment 7 FIG.
FIG. 16 is a circuit diagram showing an air conditioner 600 according to Embodiment 7 of the present invention. The seventh embodiment is different from the fifth embodiment in that the control unit 10 and the pressure detection unit 6b are provided. In the seventh embodiment, the same parts as those in the first to sixth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on the differences from the first to sixth embodiments.

As shown in FIG. 16, the pressure detector 6 b is provided on the downstream side of the refrigerant heat medium heat exchanger 26 and detects the pressure of the heat medium flowing in the heat medium circuit 3. Thus, in this Embodiment 7, the refrigerant | coolant detection part 6 has the discharge | emission refrigerant | coolant detection part 6a and the pressure detection part 6b. The pressure detector 6b may be provided on the upstream side of the refrigerant heat exchanger related to heat medium 26. The heat source device 20 is provided with a control unit 10. The control unit 10 is a microcomputer or the like that controls each device.

The control unit 10 closes the outlet side valve 7 and the inlet side valve 8 when the concentration of the refrigerant detected by the refrigerant detection unit 6 exceeds a preset threshold value. Moreover, the control part 10 may stop the pump 32, when the density | concentration of the refrigerant | coolant detected by the refrigerant | coolant detection part 6 exceeds the preset threshold value. In the seventh embodiment, specifically, when the pressure of the heat medium detected by the pressure detector 6b exceeds a preset pressure threshold, the outlet side valve 7 and the inlet side valve 8 are closed. For example, when the heat medium is water, the volume of the refrigerant expands about 37 times when the liquid refrigerant is vaporized in R32 that is in a saturated liquid state when the water pressure is 1.0 [MPaA]. In this manner, the pressure of the heat medium rapidly increases as the volume of the refrigerant expands. Thus, it is possible to detect that the refrigerant has flowed into the heat medium circuit 3 by using the pressure detection unit 6b.

When the refrigerant flows into the heat medium circuit 3, the refrigerant passes from the refrigerant heat medium heat exchanger 26 to the separation unit 4 through the heat medium pipe 31. At this time, even if the refrigerant flows into the heat medium pipe 31 from the separation unit 4, the control unit 10 closes the outlet side valve 7, and thus does not proceed beyond the outlet side valve 7. For this reason, it can suppress reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. In addition, when the refrigerant flows into the heat medium circuit 3, the refrigerant may flow backward from the refrigerant heat medium heat exchanger 26. However, since the control part 10 closes the inlet side valve 8, it does not advance ahead of the inlet side valve 8. FIG. For this reason, it can suppress more reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. As described above, in the seventh embodiment, when the refrigerant flows, the heat medium circuit 3 is separated into the indoor side and the outdoor side by the outlet side valve 7 and the inlet side valve 8. It can suppress flowing into the heat medium piping 31 provided indoors through the room. In addition, when the control part 10 stops the pump 32, since a heat medium does not flow, a refrigerant | coolant does not flow. For this reason, it can suppress that a refrigerant | coolant flows in into a room | chamber interior.

Embodiment 8 FIG.
FIG. 17 is a circuit diagram showing an air conditioner 700 according to Embodiment 8 of the present invention. The eighth embodiment is different from the fifth embodiment in that the control unit 10 and the temperature detection unit 6c are provided. In the eighth embodiment, the same parts as those in the first to seventh embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on the differences from the first to seventh embodiments.

As shown in FIG. 17, the temperature detection unit 6 c is provided on the downstream side of the refrigerant heat medium heat exchanger 26 and detects the temperature of the heat medium flowing in the heat medium circuit 3. Thus, in the eighth embodiment, the refrigerant detection unit 6 includes the exhaust refrigerant detection unit 6a and the temperature detection unit 6c. The temperature detection unit 6 c may be provided on the upstream side of the refrigerant heat exchanger related to heat medium 26. The heat source device 20 is provided with a control unit 10. The control unit 10 is a microcomputer or the like that controls each device.

The control unit 10 closes the outlet side valve 7 and the inlet side valve 8 when the concentration of the refrigerant detected by the refrigerant detection unit 6 exceeds a preset threshold value. Moreover, the control part 10 may stop the pump 32, when the density | concentration of the refrigerant | coolant detected by the refrigerant | coolant detection part 6 exceeds the preset threshold value. In the eighth embodiment, specifically, when the temperature difference of the heat medium detected by the temperature detection unit 6c every predetermined time exceeds a preset temperature difference threshold, the outlet side valve 7 and the inlet Close the side valve 8. For example, when the heat medium is water and the flow rate ratio between R32 and water is 1: 4 in R32 that is in a saturated liquid state when the water pressure is 1.0 [MPaA], the liquid state refrigerant is vaporized. In addition, the water drops by about 18 [° C.]. As described above, the temperature difference of the heat medium rapidly changes as the refrigerant evaporates. Accordingly, it is possible to detect that the refrigerant has flowed into the heat medium circuit 3 by using the temperature detection unit 6c.

When the refrigerant flows into the heat medium circuit 3, the refrigerant passes from the refrigerant heat medium heat exchanger 26 to the separation unit 4 through the heat medium pipe 31. At this time, even if the refrigerant flows into the heat medium pipe 31 from the separation unit 4, the control unit 10 closes the outlet side valve 7, and thus does not proceed beyond the outlet side valve 7. For this reason, it can suppress reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. In addition, when the refrigerant flows into the heat medium circuit 3, the refrigerant may flow backward from the refrigerant heat medium heat exchanger 26. However, since the control part 10 closes the inlet side valve 8, it does not advance ahead of the inlet side valve 8. FIG. For this reason, it can suppress more reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. As described above, in the eighth embodiment, when the refrigerant flows in, the heat medium circuit 3 is separated into the indoor side and the outdoor side by the outlet side valve 7 and the inlet side valve 8. It can suppress flowing into the heat medium piping 31 provided indoors through the room. In addition, when the control part 10 stops the pump 32, since a heat medium does not flow, a refrigerant | coolant does not flow. For this reason, it can suppress that a refrigerant | coolant flows in into a room | chamber interior.

Embodiment 9 FIG.
FIG. 18 is a circuit diagram showing an air conditioner 800 according to Embodiment 9 of the present invention. The ninth embodiment is different from the fifth embodiment in that the control unit 10 and the current detection unit 6d are provided, and the pump 32 is provided on the downstream side of the heat source side heat exchanger 24. In the ninth embodiment, the same parts as those in the first to eighth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first to eighth embodiments.

As shown in FIG. 18, the current detection unit 6 d detects the operating current of the pump 32. Thus, in the ninth embodiment, the refrigerant detection unit 6 includes the exhaust refrigerant detection unit 6a and the current detection unit 6d. The heat source device 20 is provided with a control unit 10. The control unit 10 is a microcomputer or the like that controls each device.

The control unit 10 closes the outlet side valve 7 and the inlet side valve 8 when the concentration of the refrigerant detected by the refrigerant detection unit 6 exceeds a preset threshold value. Moreover, the control part 10 may stop the pump 32, when the density | concentration of the refrigerant | coolant detected by the refrigerant | coolant detection part 6 exceeds the preset threshold value. In the ninth embodiment, specifically, when the difference in the current of the pump 32 detected by the current detection unit 6d every predetermined time exceeds a preset current difference threshold, the outlet side valve 7 and the inlet Close the side valve 8.

For example, when the refrigerant flows into the heat medium circuit 3, the refrigerant stays on the suction side of the pump 32, and the pump 32 runs idle, or the refrigerant flows into the heat medium circuit 3 and freezes. If this happens, the operating current of the pump 32 varies. As described above, when the refrigerant flows into the heat medium circuit 3, the operating current of the pump 32 varies. Thereby, it can be indirectly detected that the refrigerant has flowed into the heat medium circuit 3 by using the current detector 6d. The pump 32 may be provided on the upstream side of the refrigerant heat medium heat exchanger 26. Also in this case, it is possible to indirectly detect that the refrigerant has flowed into the heat medium circuit 3 by the current detection unit 6d.

When the refrigerant flows into the heat medium circuit 3, the refrigerant passes from the refrigerant heat medium heat exchanger 26 to the separation unit 4 through the heat medium pipe 31. At this time, even if the refrigerant flows into the heat medium pipe 31 from the separation unit 4, the control unit 10 closes the outlet side valve 7, and thus does not proceed beyond the outlet side valve 7. For this reason, it can suppress reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. In addition, when the refrigerant flows into the heat medium circuit 3, the refrigerant may flow backward from the refrigerant heat medium heat exchanger 26. However, since the control part 10 closes the inlet side valve 8, it does not advance ahead of the inlet side valve 8. FIG. For this reason, it can suppress more reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors.

As described above, in the ninth embodiment, when the refrigerant flows in, the heat medium circuit 3 is separated into the indoor side and the outdoor side by the outlet side valve 7 and the inlet side valve 8. It can suppress flowing into the heat medium piping 31 provided indoors through the room. In addition, when the control part 10 stops the pump 32, since a heat medium does not flow, a refrigerant | coolant does not flow. For this reason, it can suppress that a refrigerant | coolant flows in into a room | chamber interior.

Embodiment 10 FIG.
FIG. 19 is a circuit diagram showing an air conditioning apparatus 900 according to Embodiment 10 of the present invention. The tenth embodiment is different from the ninth embodiment in that the current detection unit 6d is omitted. In the tenth embodiment, the same parts as those in the first to ninth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on the differences from the first to ninth embodiments.

As shown in FIG. 19, the refrigerant detection unit 6 has only an exhausted refrigerant detection unit 6a. The heat source device 20 is provided with a control unit 10. The control unit 10 is a microcomputer or the like that controls each device.

The control unit 10 closes the outlet side valve 7 and the inlet side valve 8 when the concentration of the refrigerant detected by the refrigerant detection unit 6 exceeds a preset threshold value. Moreover, the control part 10 may stop the pump 32, when the density | concentration of the refrigerant | coolant detected by the refrigerant | coolant detection part 6 exceeds the preset threshold value. In the tenth embodiment, specifically, the outlet side valve 7 and the inlet side valve 8 are closed when the refrigerant concentration detected by the discharged refrigerant detector 6a exceeds a preset refrigerant threshold. Thus, in the tenth embodiment, the refrigerant can be directly detected. For this reason, the detection accuracy of the refrigerant can be improved.

When the refrigerant flows into the heat medium circuit 3, the refrigerant passes from the refrigerant heat medium heat exchanger 26 to the separation unit 4 through the heat medium pipe 31. At this time, even if the refrigerant flows into the heat medium pipe 31 from the separation unit 4, the control unit 10 closes the outlet side valve 7, and thus does not proceed beyond the outlet side valve 7. For this reason, it can suppress reliably that a refrigerant | coolant flows in into the heat medium piping 31 provided indoors. In addition, when the refrigerant flows into the heat medium circuit 3, the refrigerant may flow backward from the refrigerant heat medium heat exchanger 26. However, since the control part 10 closes the inlet side valve 8, it does not advance ahead of the inlet side valve 8. FIG. For this reason, it can suppress more reliably that a refrigerant | coolant flows in into the heat-medium piping 31 provided indoors.

As described above, in the tenth embodiment, when the refrigerant flows in, the heat medium circuit 3 is separated into the indoor side and the outdoor side by the outlet side valve 7 and the inlet side valve 8. It can suppress flowing into the heat medium piping 31 provided indoors through the room. In addition, when the control part 10 stops the pump 32, since a heat medium does not flow, a refrigerant | coolant does not flow. For this reason, it can suppress that a refrigerant | coolant flows in into a room | chamber interior.

Embodiment 11 FIG.
FIG. 20 is a circuit diagram showing an air conditioner 1000 according to Embodiment 11 of the present invention. The eleventh embodiment is different from the ninth embodiment in that a pressure detection unit 6b, a temperature detection unit 6c, and a relief valve 35 are provided. In the eleventh embodiment, the same parts as those in the first to tenth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first to tenth embodiments.

As shown in FIG. 20, the relief valve 35 is provided on the downstream side of the refrigerant heat medium heat exchanger 26 in the heat medium circuit 3 and is a valve for releasing the heat medium flowing in the heat medium circuit 3. In the eleventh embodiment, the refrigerant detection unit 6 includes an exhaust refrigerant detection unit 6a, a pressure detection unit 6b, a temperature detection unit 6c, and a current detection unit 6d. The heat source device 20 is provided with a control unit 10. The control unit 10 is a microcomputer or the like that controls each device.

When the refrigerant concentration detected by the refrigerant detection unit 6 exceeds a preset threshold value, the control unit 10 energizes the heating unit 9 to operate it. Moreover, the control part 10 opens the relief valve 35, when the density | concentration of the refrigerant | coolant detected by the refrigerant | coolant detection part 6 exceeds the preset threshold value. In addition, the refrigerant | coolant detection may use the discharge | emission refrigerant | coolant detection part 6a, the pressure detection part 6b, the temperature detection part 6c, or the electric current detection part 6d. .

When the refrigerant flows into the heat medium circuit 3, the refrigerant may circulate in the heat medium circuit 3 in a liquid state depending on the pressure and temperature of the heat medium flowing through the heat medium circuit 3. At this time, the liquid refrigerant flowing into the separation unit 4 is heated by the heating unit 9. As a result, the liquid refrigerant is vaporized and discharged to the outside by the separation unit 4 and the discharge unit 5. When the refrigerant flows into the heat medium circuit 3, the pressure of the heat medium and the refrigerant flowing through the heat medium circuit 3 is reduced by opening the relief valve 35. Thereby, the saturation temperature of a refrigerant | coolant falls and heat exchange is carried out with the heat medium which flows with a refrigerant | coolant. As a result, the liquid refrigerant is vaporized and discharged to the outside by the separation unit 4 and the discharge unit 5.

Embodiment 12 FIG.
FIG. 21 is a circuit diagram showing an air conditioner 1100 according to Embodiment 12 of the present invention. The twelfth embodiment includes a bypass circuit 11 and a bypass flow path switching unit 12, and is different from the eleventh embodiment in that the outlet side valve 7 and the inlet side valve 8 are omitted. In the twelfth embodiment, the same parts as those in the first to eleventh embodiments are denoted by the same reference numerals, and the description thereof is omitted. The description will focus on the differences from the first to eleventh embodiments.

21, the bypass circuit 11 is a circuit that is provided outside the air-conditioned space and connects the outlet 43 of the separation unit 4 and the upstream side of the refrigerant heat medium heat exchanger 26. The bypass flow path switching unit 12 connects the outlet 43 of the separation unit 4, the bypass circuit 11, and the upstream side of the load side heat exchanger 33, and connects the outlet 43 of the separation unit 4 and the bypass circuit 11. Or a member that switches connection between the outlet 43 of the separation unit 4 and the upstream side of the load-side heat exchanger 33. The bypass flow path switching unit 12 is configured with, for example, a three-way valve, but may be configured with two two-way valves.

The control unit 10 switches the bypass flow path switching unit 12 so that the liquid flowing out from the outlet 43 normally flows into the load side heat exchanger 33. And the control part 10 is a bypass flow-path switching part so that the liquid which flowed out from the outflow port 43 may flow into the bypass circuit 11, when the density | concentration of the refrigerant | coolant detected by the refrigerant | coolant detection part 6 exceeds the preset threshold value. 12 is switched. In addition, the refrigerant | coolant detection may use the discharge | emission refrigerant | coolant detection part 6a, the pressure detection part 6b, the temperature detection part 6c, or the electric current detection part 6d. .

When the refrigerant flows into the heat medium circuit 3, the bypass channel switching unit 12 is switched by the control unit 10 so that the liquid flowing out from the outlet 43 flows into the bypass circuit 11. As a result, the refrigerant flows together with the heat medium from the refrigerant heat medium heat exchanger 26 through the pump 32, passes through the separation unit 4, and then flows into the bypass circuit 11. And the refrigerant | coolant and heat medium which flowed into the bypass circuit 11 flow in into the refrigerant | coolant heat medium heat exchanger 26 again, without passing a room | chamber interior. Therefore, the refrigerant can be prevented from flowing into the heat medium pipe 31 provided in the room. Moreover, since the refrigerant and the heat medium circulate in the order of the refrigerant heat medium heat exchanger 26, the pump 32, the separation unit 4, and the bypass circuit 11, the refrigerant and the heat medium pass through the separation unit 4 by the number of circulations. For this reason, the more the refrigerant circulates, the more the refrigerant is discharged in the separation unit 4 and the discharge unit 5. Accordingly, it is possible to further suppress the refrigerant from flowing into the heat medium pipe 31 provided in the room.

Embodiment 13 FIG.
FIG. 22 is a circuit diagram showing an air conditioner 1200 according to Embodiment 13 of the present invention. The thirteenth embodiment is different from the twelfth embodiment in that the separation unit 4 and the discharge unit 5 are omitted. In the thirteenth embodiment, the same parts as those in the first to twelfth embodiments are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first to twelfth embodiments.

As shown in FIG. 22, the bypass circuit 11 is a circuit that is provided outside the air-conditioned space and connects the downstream side of the refrigerant heat medium heat exchanger 26 and the upstream side of the refrigerant heat medium heat exchanger 26. . In the thirteenth embodiment, since the pump 32 is provided on the downstream side of the refrigerant heat medium heat exchanger 26, the bypass circuit 11 is provided on the downstream side of the pump 32 and the refrigerant heat medium heat exchanger 26. Is connected to the side. When the pump 32 is provided on the downstream side of the refrigerant heat exchanger 26, the bypass circuit 11 connects the downstream side of the refrigerant heat exchanger 26 and the upstream side of the pump 32. . The bypass flow path switching unit 12 connects the downstream side of the pump 32, the bypass circuit 11, and the upstream side of the load side heat exchanger 33, and connects the outlet 43 of the separation unit 4 and the bypass circuit 11, or It is a member that switches the connection between the outlet 43 of the separation unit 4 and the upstream side of the load side heat exchanger 33. The bypass flow path switching unit 12 is configured with, for example, a three-way valve, but may be configured with two two-way valves.

The control unit 10 switches the bypass flow path switching unit 12 so that the heat medium conveyed from the pump 32 normally flows to the load side heat exchanger 33. Then, when the concentration of the refrigerant detected by the refrigerant detection unit 6 exceeds a preset threshold, the control unit 10 bypasses the heat medium and the refrigerant conveyed from the pump 32 so as to flow into the bypass circuit 11. The path switching unit 12 is switched. In addition, the detection of the refrigerant may use the pressure detection unit 6b, the temperature detection unit 6c, or the current detection unit 6d.

When the refrigerant flows into the heat medium circuit 3, the bypass flow path switching unit 12 is switched by the control unit 10 so that the heat medium and the refrigerant conveyed from the pump 32 flow into the bypass circuit 11. Thereby, a refrigerant | coolant flows into the bypass circuit 11 through the pump 32 from the heat exchanger 26 between refrigerant | coolant heat media with a heat medium. And the refrigerant | coolant and heat medium which flowed into the bypass circuit 11 flow in into the refrigerant | coolant heat medium heat exchanger 26 again, without passing a room | chamber interior. Therefore, the refrigerant can be prevented from flowing into the heat medium pipe 31 provided in the room. Thus, by providing the bypass circuit 11, even if the separation unit 4 and the discharge unit 5 are omitted, the refrigerant can be prevented from flowing into the heat medium pipe 31 provided in the room.

Embodiment 14 FIG.
FIG. 23 is a schematic diagram showing the sub-separation unit 13 according to Embodiment 14 of the present invention. The fourteenth embodiment is different from the fourth embodiment in that the sub-separation unit 13 is provided. In the fourteenth embodiment, the same parts as those in the first to thirteenth embodiments will be denoted by the same reference numerals and the description thereof will be omitted, and differences from the first to thirteenth embodiments will be mainly described.

As shown in FIG. 23, the sub-separation unit 13 is a member that is provided in the discharge port 51 of the discharge unit 5 and separates gas and liquid. The sub-separation unit 13 is connected to the discharge port 51 of the discharge unit 5 and is connected to a discharge pipe extending upward. The sub-separation part 13 is a tubular member, extends downward from the discharge pipe, is connected to a pipe for draining at the bottom, extends upward again from the bottom, and has a gas discharge port 13b at the upper end. Thus, the subseparation part 13 is comprised with the composite pipe | tube which traps gas. At the front end of the sub-separation unit 13, an exhaust refrigerant detection unit 6a is disposed. A liquid drain valve 14 is provided in the pipe for liquid drain.

When the refrigerant flows into the heat medium circuit 3 and is discharged from the discharge unit 5, the liquid heat medium may be slightly ejected together with the refrigerant. At this time, the ejected liquid heat medium may be applied to the discharged refrigerant detection unit 6a. In the fourteenth embodiment, the liquid heat medium discharged from the discharge unit 5 is accumulated at the bottom by the sub-separation unit 13 and flows down from the bottom to the liquid draining pipe. The liquid heat medium is discharged through the liquid drain valve 14 by opening the liquid drain valve 14. Therefore, when the refrigerant passes through the sub-separation unit 13 and is discharged from the gas discharge port 13b, the liquid heat medium is not ejected. Therefore, since the liquid heat medium is not applied to the discharged refrigerant detection unit 6a, the detection accuracy of the discharged refrigerant detection unit 6a can be maintained.

(Modification)
FIG. 24 is a schematic diagram showing a sub-separation unit 13a in a modification of the fourteenth embodiment of the present invention. In the modification, the structure of the sub-separation part 13a is different from that of the fourteenth embodiment. As shown in FIG. 24, the sub-separation part 13a of a modification is a container. The subseparation part 13a is connected to the discharge port 51 of the discharge part 5, and is connected to the discharge pipe extended upwards. The sub-separation part 13a is connected to a pipe for draining at the bottom, and a gas discharge port 13b is formed at the top. An exhausted refrigerant detector 6a is disposed at the tip of the sub-separator 13a. A liquid drain valve 14 is provided in the pipe for liquid drain.

When the refrigerant flows into the heat medium circuit 3 and is discharged from the discharge unit 5, the liquid heat medium may be slightly ejected together with the refrigerant. At this time, the ejected liquid heat medium may be applied to the discharged refrigerant detection unit 6a. In the modification, the liquid heat medium discharged from the discharge unit 5 is accumulated at the bottom by the sub-separation unit 13a, and flows down from the bottom to the liquid draining pipe. The liquid heat medium is discharged through the liquid drain valve 14 by opening the liquid drain valve 14. Accordingly, when the refrigerant passes through the sub-separation part 13a and is discharged from the gas discharge port 13b, the liquid heat medium is not ejected. Therefore, since the liquid refrigerant is not applied to the exhaust refrigerant detection unit 6a, the detection accuracy of the exhaust refrigerant detection unit 6a can be maintained as in the fourteenth embodiment.

1 air conditioner, 2 refrigerant circuit, 3 heat medium circuit, 4, 4a, 4b, 4c, 4d separation unit, 5 discharge unit, 6 refrigerant detection unit, 6a discharge refrigerant detection unit, 6b pressure detection unit, 6c temperature detection unit 6d current detection unit, 7 outlet side valve, 8 inlet side valve, 9 heating unit, 10 control unit, 11 bypass circuit, 12 bypass flow path switching unit, 13, 13a sub-separation unit, 13b gas discharge port, 14 drainage Valve, 20 Heat source machine, 21 Refrigerant pipe, 22 Compressor, 23 Flow path switching device, 24 Heat source side heat exchanger, 25 Expansion section, 26 Refrigerant heat medium heat exchanger, 30 Heating / cooling appliance, 31 Heat medium pipe, 32 Pump, 33 load side heat exchanger, 34 air vent valve, 35 relief valve, 41 connection port, 41a lower end, 42 discharge port, 43 outflow port, 43a upper end, 44 extension Part, 45 discharge part, 46 outflow part, 51 outlet, 100, 100a, 100b air conditioner, 200 air conditioner, 300 air conditioner, 400 air conditioner, 600 air conditioner, 700 air conditioner, 800 air Conditioner, 900 Air conditioner, 1000 Air conditioner, 1100 Air conditioner, 1200 Air conditioner.

Claims (27)

1. A refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion section, and a refrigerant heat medium heat exchanger are connected by a refrigerant pipe and the refrigerant circulates;
   A heat exchanger between the refrigerant heat medium, a load side heat exchanger that exchanges heat with air in the air-conditioned space, is connected by a heat medium pipe, and the heat medium circulates.
   The refrigerant and the heat medium are provided outside the air-conditioned space in the heat medium pipe through which the heat medium flows out from the refrigerant heat medium heat exchanger and flows into the load-side heat exchanger. And a separation unit that separates
   A discharge unit connected to the separation unit and configured to discharge the refrigerant separated by the separation unit to the outside of the air-conditioned space;
   An air conditioner.
2. The flow path cross-sectional area of the separation part is
   The air conditioner according to claim 1, wherein the air conditioner is larger than a cross-sectional area of the heat medium pipe.
3. In the separation part,
   A connection port connected to the downstream side of the heat exchanger related to the refrigerant heat medium in the heat medium circuit;
   A discharge port connected to the discharge unit and discharging the refrigerant to the discharge unit;
   The air conditioner according to claim 1 or 2, wherein an outlet port connected to an upstream side of the load side heat exchanger in the heat medium circuit and from which the heat medium flows out is formed.
4. The separation unit is
   An extending portion extending upward from the connection port and extending laterally from the upper end;
   An outflow part extending downward from the extension part and connected to the outlet;
   The air conditioner according to claim 3, further comprising: a discharge portion provided above the outflow portion and connected to the discharge port.
5. The connection port is
   The air conditioner according to claim 3 or 4, wherein the air conditioner is formed at a position above the outlet in the height direction.
6. The lower end of the connection port is
   The air conditioner according to claim 5, wherein the air conditioner is formed at a position above the upper end of the outlet in the height direction.
7. The air conditioner according to any one of claims 1 to 6, further comprising an outlet-side valve that is provided on the downstream side of the separation unit outside the air-conditioned space and adjusts the flow rate of the heat medium.
8. The air conditioner according to any one of claims 1 to 7, further comprising an inlet side valve that is provided on the upstream side of the separation unit outside the air-conditioned space and adjusts the flow rate of the heat medium.
9. The pump is
   The air conditioner according to any one of claims 1 to 8, wherein the air conditioner is provided on a downstream side of the refrigerant heat exchanger related to heat medium.
10. The air conditioner according to any one of claims 1 to 9, further comprising a heating unit that is provided in the separation unit and heats the liquid in the separation unit.
11. The air conditioner according to any one of claims 1 to 10, further comprising a sub-separation unit that is provided in the discharge unit and separates gas and liquid.
12. The bypass circuit that is provided outside the air-conditioned space and further connects the outlet of the separation unit and the upstream side of the refrigerant heat exchanger related to heat medium. Air conditioner.
13. The outlet of the separation unit, the bypass circuit, and the upstream side of the load-side heat exchanger are connected, the connection of the outlet of the separation unit and the bypass circuit, or the flow of the separation unit The air conditioning apparatus according to claim 12, further comprising a bypass flow path switching unit that switches connection between an outlet and an upstream side of the load-side heat exchanger.
14. The air conditioner according to any one of claims 1 to 13, further comprising a relief valve provided in the heat medium circuit outside the air-conditioned space and allowing the heat medium flowing through the heat medium circuit to escape.
15. The air conditioner according to any one of claims 1 to 14, further comprising a refrigerant detector that detects that the refrigerant has flowed into the heat medium circuit.
16. The air conditioning apparatus according to claim 15, further comprising a control unit that closes the outlet-side valve when a concentration of the refrigerant detected by the refrigerant detection unit exceeds a preset threshold value.
17. The air conditioning apparatus according to claim 15 or 16, further comprising a control unit that closes the inlet valve when a concentration of the refrigerant detected by the refrigerant detection unit exceeds a preset threshold value.
18. The control unit according to any one of claims 15 to 17, further comprising a control unit that operates the heating unit when the concentration of the refrigerant detected by the refrigerant detection unit exceeds a preset threshold value. The air conditioning apparatus described.
19. A controller that switches the bypass flow path switching unit so that the liquid flowing out from the outlet flows into the bypass circuit when the concentration of the refrigerant detected by the refrigerant detection unit exceeds a preset threshold value; The air conditioning apparatus according to any one of claims 15 to 18, which is dependent on the thirteenth aspect.
20. The control unit according to any one of claims 15 to 19, further comprising a control unit that opens the relief valve when a concentration of the refrigerant detected by the refrigerant detection unit exceeds a preset threshold value. Air conditioner.
21. The refrigerant detector is
    The air conditioner according to any one of claims 15 to 20, further comprising an exhaust refrigerant detection unit that is provided in the exhaust unit and detects refrigerant discharged from the exhaust unit.
22. The refrigerant detector is
    The air conditioner according to any one of claims 15 to 21, further comprising a pressure detection unit configured to detect a pressure of the heat medium flowing through the heat medium circuit.
23. The refrigerant detector is
    The air conditioner according to any one of claims 15 to 22, further comprising a temperature detection unit configured to detect a temperature of the heat medium flowing in the heat medium circuit.
24. The refrigerant detector is
    The air conditioner according to any one of claims 15 to 23, further comprising a current detection unit that detects an operation current of the pump.
25. The separation unit is
    The air conditioner according to any one of claims 1 to 24, having a flow path cross-sectional area in which an internal flow velocity is 1500 mm / s or less.
26. The air conditioner according to any one of claims 1 to 25, wherein the heat medium separated by the separation unit flows into the load-side heat exchanger.
27. A refrigerant circuit in which a compressor, a heat source side heat exchanger, an expansion section, and a refrigerant heat medium heat exchanger are connected by a refrigerant pipe and the refrigerant circulates;
    A heat medium circuit in which a pump, a heat exchanger between the refrigerant heat medium, a load side heat exchanger that exchanges heat with air in an air-conditioned space is connected by a heat medium pipe, and the heat medium circulates;
    A bypass circuit provided outside the air-conditioned space, and connecting a downstream side of the refrigerant heat exchanger related to heat exchanger and an upstream side of the refrigerant heat exchanger related to the heat exchanger;
    An air conditioner comprising:

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