JP4867335B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner that performs heating and / or refrigerant.

  2. Description of the Related Art Conventional air conditioners include a compressor that compresses refrigerant, a condenser that condenses high-pressure refrigerant compressed by the compressor and advances liquefaction, and an expansion valve that expands the refrigerant that has been liquefied. It has been. In the expansion valve, the kinetic energy of the refrigerant is eventually discarded as thermal energy as a vortex and the like, so there is a limit to improving the energy efficiency.

  Therefore, Patent Document 1 discloses a refrigeration cycle in which an ejector is incorporated instead of an expansion valve in order to recover the kinetic energy of the refrigerant as much as possible. According to this, the kinetic energy by the drive flow of an ejector is converted into the pressurization work of a suction flow. By converting the energy at the time of expansion into velocity energy in the ejector, it is possible to recover the energy by increasing the pressure of the refrigerant, and to improve the energy efficiency. Further, the refrigerant on the inlet side of the flow rate control means in the mainstream refrigerant route is supercooled by the expanded refrigerant. According to this, it is assumed that the refrigerant before being expanded by the ejector is in a liquid phase state.

Patent Document 2 discloses a refrigeration cycle incorporating an ejector. The refrigeration cycle includes a compressor that is driven by a drive source to compress refrigerant, a condenser that condenses high-pressure refrigerant compressed by the compressor to advance liquefaction, an ejector that expands the refrigerant that has undergone liquefaction, and an ejector from the ejector. An evaporator having a separator for separating the liquid-phase refrigerant and the gas-phase refrigerant of the gas-liquid mixed refrigerant, an inlet through which the liquid-phase refrigerant flows into the separator, and an outlet connected to the suction flow path of the ejector. And.
JP 2003-83620 A Japanese Patent Laid-Open No. 10-205898

  According to the devices according to Patent Documents 1 and 2 described above, it is required to further reduce the power consumption of the compressor.

  This invention is made | formed in view of the above-mentioned actual condition, and makes it a subject to provide the air conditioning apparatus advantageous to further reducing the power consumption of a compressor, using an ejector.

  (1) The present inventor firstly states that the amount of energy that can be recovered in the adiabatic expansion process of the refrigerant depends on the magnitude of the enthalpy difference generated in the adiabatic expansion process, and secondly, in the ejector cycle, the speed of the refrigerant Is V, and the enthalpy difference during expansion is Δh, it is basically expressed as V = sqrt (2 · Δh) by the energy balance equation, and the kinetic energy (velocity energy) of the refrigerant is If the enthalpy difference Δh can be converted into an enthalpy difference Δh, the kinetic energy (velocity energy) of the refrigerant increases and the energy that can be recovered increases. Third, from the outlet of the condenser, the drive path of the ejector If the refrigerant supplied to the inlet is in a two-phase state of a liquid phase and a gas phase rather than only in the liquid phase state, the enthalpy difference Δh at the time of adiabatic expansion can be increased. Increased coolant kinetic energy (speed energy), paying attention to the fact that the energy that can be recovered increases, and completed the present invention based on such interest.

(2) An air conditioner according to the present invention includes a compressor driven by a drive source to compress the refrigerant,
A condenser that condenses the high-pressure refrigerant compressed by the compressor and advances liquefaction;
A mixed flow is formed by mixing the drive flow path for flowing the liquefied refrigerant, the suction flow path for sucking the suction flow by the refrigerant flowing through the drive flow path, and the refrigerant flowing through the drive flow path and the suction flow flowing through the suction flow path An ejector having a mixing flow path;
A separator for separating the liquid phase and the gas phase of the mixed flow mixed by the ejector;
In an air conditioner including an evaporator for evaporating a liquid phase of a refrigerant having an inlet through which a liquid phase of a separator flows and an outlet connected to a suction flow path of an ejector,
Gas-liquid two-phase stabilization means for stably maintaining the refrigerant supplied from the outlet of the condenser to the inlet of the drive flow path of the ejector in a two-phase state of a liquid phase and a gas phase is provided with the outlet of the condenser and the ejector. Between the inlet of the drive flow path of
The homogenizing means for proceeding the homogenization of the two-phase state of the liquid phase and the gas phase of the refrigerant supplied from the condenser to the ejector via the gas-liquid two-phase state stabilizing means is a gas-liquid two-phase state stabilizing means. characterized in that it kicked set between the ejector.

  (3) The high-temperature and high-pressure refrigerant compressed by the compressor is condensed by heat radiation in the condenser and advances liquefaction. The liquefied refrigerant is supplied to the ejector and expands (adiabatic expansion) through the ejector drive flow path. The refrigerant supplied from the ejector to the separator is a mixture of a liquid phase and a gas phase. The separator separates the liquid phase and the gas phase. The gas phase separated from the refrigerant by the separator is supplied to the compressor, compressed and pressurized again, and supplied to the condenser again. The liquid phase separated by the separator among the refrigerant is supplied to the evaporator and used for expansion in the evaporator. Here, if the evaporator is on the indoor unit side, the room is cooled. If the condenser is on the indoor unit side, the room is heated.

  By the way, the liquefied refrigerant is supplied to the ejector and expands (adiabatically expands) through the drive flow path of the ejector. At this time, the refrigerant evaporated by the evaporator and vaporized is sucked as a suction flow into the ejector from the suction passage of the ejector. The drive flow that flows through the drive flow path of the ejector and the suction flow sucked from the suction flow path of the ejector are mixed in the mixing flow path of the ejector to become a mixed flow. In this case, since the pressure of the mixed flow increases as compared with the case where the suction flow is not sucked, the pressure of the gas phase of the refrigerant supplied to the suction port of the compressor increases. For this reason, the power consumption of a compressor is reduced and it can contribute to energy saving.

According to the present invention, the gas-liquid two-phase state stabilizing means is provided in the flow path connecting the outlet of the condenser and the inlet of the drive flow path of the ejector. For this reason, the refrigerant supplied from the outlet of the condenser to the inlet of the drive channel of the ejector can be stably maintained in a gas-liquid two-phase state in which the liquid phase and the gas phase are in a two-phase state.

  According to the present invention, the refrigerant supplied from the outlet of the condenser to the inlet of the drive flow path of the ejector via the gas-liquid two-phase state stabilizing means is more liquid-phase than the liquid-phase state (single-phase flow). A two-phase state with the gas phase can be stably formed. Thereby, the enthalpy difference Δh at the time of adiabatic expansion can be increased according to the characteristics of the Mollier diagram, according to the refrigerant in the two-phase state of the liquid phase and the gas phase, compared to the refrigerant in the liquid phase state (single phase flow) only. Since the enthalpy difference Δh increases in this way, the kinetic energy (velocity energy) of the refrigerant increases by the energy balance equation (V = sqrt (2 · Δh). This increases the refrigerant pressure on the suction side of the compressor. As a result, the power consumption of the compressor is reduced.

Furthermore, according to the present invention, the homogenizing means for proceeding the homogenization of the two-phase state of the liquid phase and the gas phase of the refrigerant supplied from the condenser to the ejector through the gas-liquid two-phase state stabilizing means includes the gas-liquid It is kicked set between the two-phase state stabilization means and the ejector. By such a homogenizing means, the homogenization in the two-phase state of the liquid phase and the gas phase of the refrigerant supplied from the condenser to the ejector through the gas-liquid two-phase state stabilizing means can be advanced. Thus, the two-phase state (two-phase state) of the liquid phase and the gas phase is refined and homogenized.

According to the present invention, the gas-liquid two-phase state stabilizing means converts the refrigerant supplied from the outlet of the condenser to the inlet of the drive channel of the ejector through the gas-liquid two-phase state stabilizing means. A refrigerant in a two-phase state of a liquid phase and a gas phase can be formed more stably than a refrigerant having only a (phase flow) and supplied to the drive flow path of the ejector. Thereby, the enthalpy difference Δh at the time of adiabatic expansion can be made larger than that of the refrigerant only in the liquid phase state (single phase flow). Since the enthalpy difference Δh increases in this way, the energy balance equation (V = sqrt (2 · Δh) increases the kinetic energy (velocity energy) of the refrigerant, thereby increasing the refrigerant pressure on the suction side of the compressor. The power consumption of the compressor is reduced.

Furthermore, according to the present invention, the homogenizing means for proceeding the homogenization of the two-phase state of the liquid phase and the gas phase of the refrigerant supplied from the condenser to the ejector through the gas-liquid two-phase state stabilizing means includes the gas-liquid It is kicked set between the two-phase state stabilization means and the ejector. By such a homogenizing means, the homogenization in the two-phase state of the liquid phase and the gas phase of the refrigerant supplied from the condenser to the ejector through the gas-liquid two-phase state stabilizing means can be advanced. Thus, the two-phase state (two-phase state) of the liquid phase and the gas phase is refined and homogenized. Thereby, the conversion efficiency which converts enthalpy difference (DELTA) h into the speed energy of a refrigerant | coolant improves.

  The compressor is driven by a driving source to compress the refrigerant. Examples of the refrigerant include a fluorocarbon type, a hydrocarbon type, and a carbon dioxide type. Examples of the drive source include an engine or an electric motor. The engine may be a gas engine driven by gas fuel or an engine driven by liquid fuel. The ejector is a mixture that forms a mixed flow by mixing the driving flow path through which the liquefied refrigerant flows, the suction flow path for sucking the suction flow, and the refrigerant flowing through the drive flow path and the suction flow flowing through the suction flow path And a flow path. The separator separates the liquid phase and the gas phase of the mixed flow mixed by the ejector. The evaporator has an inlet through which the liquid phase of the separator flows and an outlet connected to the suction flow path of the ejector, and evaporates the liquid phase of the refrigerant.

  The gas-liquid two-phase state stabilization means is provided in a flow path that connects the outlet of the condenser and the inlet of the drive flow path of the ejector. The gas-liquid two-phase state stabilizing means stabilizes the refrigerant supplied from the outlet of the condenser to the inlet of the drive channel of the ejector in a two-phase state of a liquid phase and a gas phase instead of only the liquid phase. To maintain.

  The gas-liquid two-phase state stabilization means preferably includes a variable flow rate mechanism that varies the flow rate of the refrigerant supplied from the outlet of the condenser to the inlet of the drive channel of the ejector. The flow rate variable mechanism is preferably formed by at least one of a flow rate control valve having a variable opening degree and a fluid throttle having a variable opening degree.

  Preferably, the gas-liquid two-phase state stabilization unit includes a first temperature detection unit that detects a temperature TA of the refrigerant upstream of the flow rate variable mechanism, and a second temperature detection that detects a temperature TB of the refrigerant downstream of the flow rate variable mechanism. And when the TA-TB is equal to or higher than a predetermined temperature (generally 0 ° C. or higher), the opening degree of the flow rate variable mechanism is increased, and the refrigerant flow rate downstream of the flow rate variable mechanism is increased. Here, when the refrigerant supplied to the ejector is in a two-phase state, the temperature TA and the temperature TB approach (preferably become equal). On the other hand, when the refrigerant supplied to the ejector is in a liquid phase state (one phase state), TA> TB, and TA-TB is equal to or higher than a predetermined temperature (generally 0 ° C.). Therefore, when TA-TB is equal to or higher than a predetermined temperature (generally 0 ° C. or higher), the gas-liquid two-phase state stabilizing means increases the opening of the flow rate variable mechanism to reduce the refrigerant flow rate downstream of the flow rate variable mechanism. increase. Thereby, the gas-liquid two-phase state of a refrigerant | coolant is accelerated | stimulated and temperature TA and temperature TB approach. Preferably, the temperature TA and the temperature TB are equal.

  Further, the gas-liquid two-phase state stabilizing means has light detecting means for optically detecting the state of the refrigerant supplied to the drive flow path of the ejector, and is optically in the liquid phase state (single phase state). When judged, the form which increases the opening degree of a flow variable mechanism is illustrated.

The homogenizing means for proceeding the homogenization of the two-phase state of the liquid phase and the gas phase of the refrigerant supplied to the ejector via the gas-liquid two-phase state stabilizing means is provided between the gas-liquid two-phase state stabilizing means and the ejector. It has been kicked set in between. Preferably, homogenizing means is a pore held member having pores. Since the liquid phase is separated and the gas phase is separated by the pores, the two-phase state (two-phase state) of the liquid phase and the gas phase is refined and homogenized. Thereby, the conversion efficiency which converts enthalpy difference (DELTA) h into the speed energy of a refrigerant | coolant improves. Examples of the pore-retaining member include a net-like member, a fiber aggregate, and a particle aggregate. Examples of the fiber include glass fiber, carbon fiber, and metal fiber. The mesh member is exemplified by a strainer. One strainer may be used, or a plurality of strainers may be arranged in parallel in the flow direction of the refrigerant. A plurality of sheet-like net members may be laminated. Examples of the particles include metal balls, resin balls, ceramic balls, and the like.

  Embodiment 1 of the present invention will be specifically described below with reference to FIGS. The first refrigerant circuit 100 of the air conditioner is driven by an engine as a drive source and compresses a gas-phase refrigerant, and the high-temperature and high-pressure refrigerant compressed by the compressor 102 is condensed to advance liquefaction. The condenser 104, the ejector 106 having a function of expanding (adiabatic expansion) the refrigerant that has been liquefied, and the separator 114 that separates the liquid phase and the gas phase of the gas-liquid mixed refrigerant discharged from the ejector 106 are connected. The compressor 102 has a suction port 102 a connected to the gas phase of the separator 114 and a discharge port 102 c connected to the condenser 104. A fan 116 that supplies air to the condenser 104 to cool the condenser 104 is provided in the vicinity of the condenser 104. The second refrigerant circuit 200 of the air conditioner is connected to the first refrigerant circuit 100. The second refrigerant circulation path 200 connects the liquid phase portion of the separator 114 and the suction flow path 109 of the ejector 106, and has an evaporator 202. The evaporator 202 has an inlet 202 i into which the liquid phase of the refrigerant stored in the separator 114 flows and an outlet 202 o connected to the ejector 106. The liquid phase of the refrigerant stored in the separator 114 expands in the evaporator 202.

  FIG. 2 shows the internal structure of the ejector 106. As shown in FIG. 2, the ejector 106 includes a nozzle portion 108 that forms a driving flow path 107 through which the refrigerant that has been liquefied in the condenser 104 expands (adiabatic expansion), and an outlet 202 o of the evaporator 202. The connecting portion 110 connected to the suction flow path 109 that sucks the gas-phase refrigerant discharged from the suction flow as a suction flow, and the drive flow M1 flowing through the drive flow path 107 and the suction flow M2 flowing through the suction flow path 109 are mixed and mixed. And a mixing channel 111 that forms Since the driving flow and the suction flow merge in the mixing channel 111, the pressure of the refrigerant increases. Note that the mixing flow path 111 forming the mixed flow has a conical diffuser portion 112 in which the flow path increases toward the downstream.

  As shown in FIG. 1, a gas-liquid two-phase state stabilizing unit 300 is provided in the intermediate flow path 301 that connects the outlet of the condenser 104 and the inlet of the drive flow path 107 of the ejector 106. Therefore, the refrigerant supplied from the outlet of the condenser 104 to the inlet of the drive channel 107 of the ejector 106 is in a gas-liquid two-phase state (a two-phase state of a liquid phase and a gas phase) in which the liquid phase and the gas phase are mixed. ) Can be stably maintained.

  The gas-liquid two-phase state stabilizing means 300 stably forms the refrigerant supplied from the outlet of the condenser 104 to the inlet of the drive channel 107 of the ejector 106 in a two-phase state of a liquid phase and a gas phase. A first flow rate control valve 302 as a flow rate variable mechanism, and a control unit 308 for controlling the first flow rate control valve 302. The first flow control valve 302 has a predetermined opening when the refrigerant flows.

  Furthermore, the gas-liquid two-phase state stabilization means 300 includes a first temperature sensor 303 (first temperature detection means) that detects the refrigerant temperature TA upstream of the first flow control valve 302, and a first flow control valve 302. A second temperature sensor 305 (second temperature detecting means) that detects the temperature TB of the downstream refrigerant, and the first flow rate control when TA-TB is equal to or higher than a predetermined temperature (generally 0 ° C. or higher). The opening degree of the valve 302 is increased, and the flow rate of the refrigerant flowing through the first flow rate control valve 302 is increased. As a result, the refrigerant at the stage before being supplied to the ejector 106 (that is, the refrigerant state shown in (3) in the Mollier diagram shown in FIG. 3) moves to the arrow S1 direction side in the Mollier diagram, A gas-liquid two-phase state in which the liquid phase exists more stably is obtained.

  When there is a tolerance in temperature measurement by the first temperature sensor 303 and the second temperature sensor 305, the tolerance can be corrected. When the tolerance is not corrected, even if TA-TB is 0 ° C., it may not be 0 ° C. due to the tolerance.

  Here, when the refrigerant is in a two-phase state, the temperature TA and the temperature TB approach (preferably become equal). On the other hand, when the refrigerant is in a liquid phase only state (one phase state), TA> TB, and TA-TB is equal to or higher than a predetermined temperature (generally 0 ° C.). Therefore, when TA-TB is equal to or higher than a predetermined temperature (generally 0 ° C. or higher), the gas-liquid two-phase state stabilization means 300 increases the opening degree of the first flow control valve 302 and the first flow control valve 302. Increase the flow rate of the refrigerant that permeates. As a result, the temperature TA and the temperature TB approach each other and become equal.

  According to the present embodiment, the high-temperature and high-pressure refrigerant compressed by the compressor 102 is condensed by heat dissipation in the condenser 104 and liquefaction proceeds. The refrigerant that has been liquefied by the condenser 104 is supplied to the drive flow path 107 of the ejector 106 and flows through the drive flow path 107 of the ejector 106. At this time, the liquefied refrigerant expands (adiabatic expansion).

  The gas-liquid two-phase refrigerant discharged from the outlet of the drive channel 107 of the ejector 106 is supplied to the separator 114 and separated into a liquid phase and a gas phase by the separator 114. The gas phase separated by the separator 114 out of the refrigerant is sucked into the suction port 102a of the compressor 102, is compressed again by the compressor 102, is increased in pressure, and is supplied again to the condenser 104 from the discharge port 102c.

  On the other hand, the liquid phase separated by the separator 114 in the refrigerant is supplied to the evaporator 202 from the inlet 202i of the evaporator 202 via the second flow rate control valve 400, and expands in the evaporator 202 to form a gas phase. Become. The refrigerant that has become a gas phase is discharged from the outlet 202o of the evaporator 202, and is sucked into the suction flow path 109 of the ejector 106 as a suction flow.

  Here, the refrigerant that has been liquefied in the condenser 104 is supplied to the drive channel 107 of the ejector 106 and expanded. At this time, the refrigerant evaporated by the evaporator 202 and vaporized is sucked into the ejector 106 from the suction flow path 109 of the ejector 106 as a suction flow. The drive flow M1 flowing through the drive flow path 107 of the ejector 106 and the suction flow M2 sucked from the suction flow path 109 of the ejector 106 are mixed in the mixing flow path 111 of the ejector 106 to become a mixed flow. In this case, the pressure of the mixed flow increases as compared with the case where the suction flow is not sucked into the ejector 106. For this reason, the gas phase pressure of the refrigerant supplied to the suction port 102a of the compressor 102 increases. For this reason, the power consumption of the compressor 102 is reduced, which can contribute to energy saving.

  According to the present embodiment, if the condenser 104 having heat dissipation is on the indoor unit side, the indoor unit has a heating function. If the endothermic evaporator 202 is on the indoor unit side, the indoor unit has a cooling function. The condenser 104 is on the indoor unit side, and the condenser 104 is used as the heating side during heating. In cooling, the flow path is switched by a flow path switching valve (not shown), and if the condenser 104 on the indoor unit side is used as an evaporator and the evaporator 202 is used as a condenser, the indoor unit functions as cooling. You can also.

3 and 4 are Mollier diagrams showing the state of the refrigerant. 3 and 4, the horizontal axis represents enthalpy, and the vertical axis represents refrigerant pressure. In the Mollier line, the region on the left side of the characteristic line SA corresponds to the liquid phase state (L). A region surrounded by the characteristic line SA and the characteristic line SB corresponds to a gas-liquid two-phase state (G + L). Region of the right side of the characteristic line SB corresponds to a gas phase (G) (see FIG. 4).

  Reference numerals (1) to (9) on the refrigerant circuit in FIG. 1 correspond to the states of reference numerals (1) to (9) in the Mollier diagram shown in FIG. That is, the refrigerant sucked into the compressor 102 is in the state shown in (1). By the compression process by the compressor 102, the refrigerant changes from the state shown in (1) to the state shown in (2), and the enthalpy increases as the pressure increases. In this cycle, pressure and enthalpy are highest in the state shown in (2). Due to the condensing step in the condenser 104, the refrigerant is changed from the state (2) to the state (3), and the enthalpy is reduced while the pressure is constant. Thereby, liquefaction advances with the high pressure. The high-pressure refrigerant that has been liquefied is changed from the state shown in (3) to the state shown in (4) by the expansion process (adiabatic expansion) in the ejector 106 that functions as an expansion element, and is decompressed and expanded (adiabatic expansion). . The state shown in (4) is a gas-liquid two-phase state of the refrigerant. The driving flow of the refrigerant flowing through the driving flow path 107 of the ejector 106 is in the state shown in (4), that is, the gas-liquid two-phase state. The suction flow sucked from the suction flow path 109 of the ejector 106 is in the state shown in (9) (gas phase state). The driving flow and the suction flow merge at the tip end portion 108c of the nozzle portion 108 of the ejector 106 (start of merging corresponds to point X in FIG. 3). Since the merging gradually proceeds in the mixing flow path 111 of the ejector 106, the refrigerant moves from the point X to the state shown in (5) in FIG.

  The refrigerant whose pressure is increased to the state shown in (5) is separated into a gas phase and a liquid phase by the separator 114. The separated gas phase corresponds to the state shown in (1). The separated gas phase is sucked and compressed by the compressor 102 by the suction force of the compressor 102, and changes from the state shown in (1) to the state shown in (2). On the other hand, the liquid phase separated by the separator 114 corresponds to the state shown in (6) on the characteristic line SA. The liquid phase of the separator 114 is depressurized by the second flow control valve 400, enters the state shown in (7), and is supplied to the evaporator 202. When the refrigerant in the state shown in (7) is evaporated by the evaporator 202 and the vaporization proceeds, the state shown in (8) is obtained.

  Here, in the Mollier diagram shown in FIG. 4, a1 → b1, a2 → b2, and a3 → b3 all indicate the adiabatic expansion process of the refrigerant. a1, a2, and a3 indicate states before the adiabatic expansion in the ejector 106, and correspond to the refrigerant state at the inlet of the drive channel 107 of the ejector 106. b1, b2, and b3 correspond to refrigerant states after adiabatic expansion in the ejector 106. In FIG. 4, the enthalpy difference of a1 → b1 is shown as Δh1. The enthalpy difference of a2 → b2 is shown as Δh2. The enthalpy difference of a3 → b3 is shown as Δh3. In the Mollier diagram shown in FIG. 4, the isentropic line is inclined in the direction in which the person goes to the direction of the arrow S <b> 1 rather than the characteristic line SA. For this reason, the enthalpy difference Δh increases in the Mollier diagram when the adiabatic expansion process described above shifts in the direction of the arrow S1. That is, the relationship Δh1 <Δh2 <Δh3 is established. Here, a1 → b1 corresponds to a process of adiabatic expansion of the liquid phase refrigerant. a2 → b2 corresponds to a process of adiabatic expansion of the refrigerant in the gas-liquid two-phase state. a3 → b3 corresponds to the process of adiabatic expansion of the refrigerant in the gas-liquid two-phase state.

  According to this embodiment, when the refrigerant supplied from the outlet of the condenser 104 to the inlet of the drive flow path 107 of the ejector 106 is in a liquid phase (single phase) state, the opening degree of the first flow control valve 302 is increased. Let Thereby, the refrigerant supplied from the outlet of the condenser 104 to the inlet of the drive channel 107 of the ejector 106 is in a gas-liquid two-phase state (gas-liquid mixed state) in which the liquid phase and the gas phase are mixed. As a result, in the Mollier diagram shown in FIG. 4, the state of the refrigerant supplied to the inlet of the drive channel 107 of the ejector 106 shifts in the direction of arrow S1. That is, the refrigerant supplied to the ejector 106 changes from a liquid phase state (one-phase state) to a stable gas-liquid two-phase state (gas-liquid mixed state). As a result, the enthalpy difference Δh in the adiabatic expansion process increases. Therefore, the velocity energy of the refrigerant is increased by the energy balance equation (V = sqrt (2 · Δh). As a result, the pressure of the refrigerant sucked into the suction port of the compressor 102 increases. As a result, the power consumption of the compressor 102 is reduced. Thus, energy saving of the power of the compressor 102 can be achieved.

According to this embodiment, as shown in FIG. 5, the gas-liquid two-phase state supplied from the outlet of the condenser 104 to the inlet of the drive channel 107 of the ejector 106 through the gas-liquid two-phase state stabilizing means 300. A strainer 500 that functions as a homogenizing means for proceeding the homogenization of the refrigerant is provided. The strainer 500 is provided between the outlet of the condenser 104 (gas-liquid two-phase state stabilization means 300) and the inlet of the drive channel 107 of the ejector 106. That is, the strainer 500 is provided between the first flow rate control valve 302 that is a component of the gas-liquid two-phase state stabilization unit 300 and the inlet of the drive flow path 107 of the ejector 106. The strainer 500 includes a net-like cylindrical member 501 having a large number of pores and a net-like tip portion 502 having a large number of pores integrally connected to the cylindrical member 501.

Even if the refrigerant supplied to the inlet of the drive flow path 107 of the ejector 106 through the gas-liquid two-phase stabilization means 300 is in the gas-liquid two-phase state, it is a slag flow in which the gas phase and the liquid phase are in a rough state. If so, the stability of the refrigerant flow may be impaired. In this respect, according to the present embodiment, even if the refrigerant supplied to the ejector 106 is a slag flow in a gas-liquid two-phase state, the gas-liquid two-phase state is caused by the pores that are the meshes of the strainer 500. Is further refined and homogenized. As a result, the liquid phase and gas phase particle sizes in the gas-liquid two-phase state are made finer, speed energy can be increased, and the conversion efficiency for converting the enthalpy difference Δh into the speed energy of the refrigerant is improved.
[Reference Example 1]

Hereinafter, Reference Example 1 of the present invention will be specifically described with reference to FIG. The reference example 1 has basically the same configuration and the same function and effect as the first embodiment. Hereinafter, the description will focus on the different parts. According to this example , as shown in FIG. 6, a strainer 500 is provided as a homogenizing means for advancing homogenization of the gas-liquid two-phase refrigerant supplied to the inlet of the drive flow path 107 of the ejector 106. Yes. The strainer 500 is incorporated in the ejector 106 (see FIG. 6) . Due to the pores of the strainer 500, the gas-liquid two-phase refrigerant is refined and further homogenized. Thereby, the conversion efficiency which converts enthalpy difference (DELTA) h into the speed energy of a refrigerant | coolant improves.
[Reference Example 2]

Hereinafter, Reference Example 2 of the present invention will be specifically described with reference to FIG. The reference example 2 has basically the same configuration and the same function and effect as the first embodiment. Hereinafter, the description will focus on the different parts. According to this example , as shown in FIG. 7, a mesh member 510 is provided as a homogenizing means for advancing the homogenization of the gas-liquid two-phase refrigerant supplied to the inlet of the drive flow path 107 of the ejector 106. ing. A plurality of mesh members 510 are arranged in series in the refrigerant flow direction. Due to the pores formed in the mesh member 510, the gas-liquid two-phase refrigerant is refined and homogenized. Thereby, the conversion efficiency which converts enthalpy difference (DELTA) h into the speed energy of a refrigerant | coolant improves.
[Reference Example 3]

Hereinafter, Reference Example 3 of the present invention will be specifically described with reference to FIG. The reference example 3 has basically the same configuration and the same function and effect as the first embodiment. Hereinafter, the description will focus on the different parts. According to this example , as shown in FIG. 8, a fiber assembly 520 is provided as a homogenizing means for advancing homogenization of the gas-liquid two-phase refrigerant supplied to the inlet of the drive flow path 107 of the ejector 106. It has been. The fiber assembly 520 is made of glass fiber. Since the refrigerant passes through gaps (pores) between the fibers formed in the fiber assembly 520, the gas-liquid two-phase refrigerant is refined and homogenized. Thereby, the conversion efficiency which converts enthalpy difference (DELTA) h into the speed energy of a refrigerant | coolant improves. Note that, instead of glass fiber, carbon fiber or metal fiber having good corrosion resistance may be used.
[Example 2 ]

The second embodiment of the present invention will be specifically described below with reference to FIG. This embodiment basically has the same configuration as that of the first embodiment. Therefore, the strainer 500 functioning as a homogenizing means is provided at the same position as that of the first embodiment. Has the same effect. Hereinafter, the description will focus on the different parts. According to the present embodiment, as shown in FIG. 9, the gas-liquid two-phase state stabilizing means 300B uses the two-phase liquid phase and gas phase for the refrigerant supplied to the inlet of the drive channel 107 of the ejector 106. The first flow rate control valve 302 serving as a variable flow rate mechanism and a control unit 308 that controls the first flow rate control valve 302 are provided to stably maintain the state. The first flow control valve 302 has a predetermined opening when the refrigerant flows. A transparent portion 301c made of transparent glass or transparent resin is formed in the passage wall of the intermediate flow path 301 connecting the condenser 104 and the ejector 106. The gas-liquid two-phase state stabilization means 300B includes an optical sensor 505 (light detection means). The light from the optical sensor 505 detects the state of the refrigerant flowing between the first flow control valve 302 and the ejector 106 (specifically, the transparent portion 301c). That is, the light from the optical sensor 505 is transmitted or reflected with respect to the transparent portion of the intermediate flow path 301, and the state of the refrigerant flowing through the transparent portion 301c is detected. A signal from the optical sensor 505 is input to the control unit 308.

  Here, the light transmission state or the light reflection state when the state of the refrigerant flowing between the first flow control valve 302 and the ejector 106 is only the liquid phase is stored in the memory of the control unit 308. The light transmission state or the light reflection state when the state of the refrigerant flowing between the first flow control valve 302 and the ejector 106 is a two-phase state of a liquid phase and a gas phase is stored in the memory of the control unit 308. ing.

When the control unit 308 determines that the state of the refrigerant flowing between the first flow control valve 302 and the ejector 106 is only the liquid phase of the refrigerant based on the signal of the optical sensor 505, the control unit 308 The opening degree of the flow control valve 302 is increased. Thereby, similarly to the case of the first embodiment, the flow rate of the refrigerant flowing through the first flow rate control valve 302 is increased.
[Example 3]

  10 and 11 are circuit diagrams of an embodiment of an engine driven heat pump type air conditioner according to the present invention. FIG. 10 shows the operating state during cooling. FIG. 11 shows the operating state during heating. As shown in FIGS. 10 and 11, the gas-liquid two-phase state stabilization means 300 stably maintains the refrigerant supplied to the ejector 15 in a two-phase state of a liquid phase and a gas phase. As in the case of the first embodiment, the gas-liquid two-phase state stabilization unit 300 detects the temperature TA of the first flow rate control valve 32 as the flow rate variable mechanism and the refrigerant upstream of the first flow rate control valve 32. 1 temperature sensor 303 (1st temperature detection means) and 2nd temperature sensor 305 (2nd temperature detection means) which detects the temperature TB of the refrigerant | coolant downstream of the 1st flow control valve 32 are provided. The gas-liquid two-phase state stabilization means 300 increases the opening degree of the first flow control valve 32 when the temperature TA−temperature TB is 0 ° C. or higher.

Furthermore, as shown in FIGS. 10 and 11, a strainer 500 is provided between the first flow control valve 32 and the ejector 15, which are components of the gas-liquid two-phase state stabilization means 300 . The strainer 500 further refines and homogenizes the gas-liquid two-phase refrigerant. Therefore, the strainer 500 can function as a homogenizing means for promoting the homogenization of the two-phase state of the liquid phase and the gas phase of the refrigerant supplied to the ejector 15.

As shown in FIGS. 10 and 11, the engine-driven heat pump air conditioner of this embodiment includes one outdoor unit 10 and a plurality of indoor units 20 that are provided in each room and can be operated and stopped individually. The control device 40 controls the operation of the both 10 and 20. The control device 40 is provided with an operating device 41 for starting / stopping the air conditioner, setting an air conditioning temperature, displaying an operating state, and the like.
The engine-driven heat pump type air conditioner of this embodiment is composed of one outdoor unit 10 installed outdoors and a plurality of indoor units 20 installed in each room. The outdoor unit 10 includes two compressors 11 (11a and 11b) driven by a gas engine (engine), a refrigerant circulation path 30 through which refrigerant supplied from the compressor 11 is circulated, and the refrigerant circulation path 30. An outdoor heat exchanger 13, a four-way valve (switching valve) 12, an ejector 15, a cooling water heat exchanger 16, an accumulator (gas-liquid separator) 17, and a supercooling heat exchanger 18 are provided. Yes. The ejector 15 forms a suction flow path 15b, a mixing flow path 15c, a diffuser 15d, and a drive flow path for ejecting the introduced refrigerant from the suction flow path 15b toward the mixing flow path 15c. It consists of the nozzle part 15a.

  Both compressors 11 are arranged in parallel, the discharge port of each compressor 11 is connected to the inlet port 12a of the four-way valve 12 by a supply line 30a of the refrigerant circulation path 30, and a separator 14 is provided in the middle of the supply line 30a. ing. The return pipe 30c having one end connected to the outlet port 12b of the four-way valve 12 has the other end connected to the suction ports of both compressors 11 through the mixing flow path 15c and the diffuser 15d from the suction flow path 15b of the ejector 15. A cooling water heat exchanger 16 and an accumulator 17 are provided between the ejector 15 and the suction port of the compressor 11. The cooling water heat exchanger 16 is formed by covering the outside of the pipe line through which the refrigerant from the ejector 15 passes with a water jacket. The water jacket circulates cooling water from a gas engine (not shown) that drives the compressor 11. The cooling water inlet 16a and the cooling water outlet 16b are provided. The accumulator 17 separates the refrigerant mixed with the gas phase and the liquid phase sent from the ejector 15 into the gas phase and the liquid phase, and the separated gas phase refrigerant is returned to the suction port of the compressor 11. It is like that. The bottom of the separator 14 communicates with a return line 30 c immediately before the compressor 11, and the oil separated from the refrigerant removes foreign matters and moisture and returns to the compressor 11.

  Circulation pipes 30b1 and 30b2 of the refrigerant circulation path 30 having one ends connected to the pair of switching ports 12c and 12d of the four-way valve 12, respectively, go out of the outdoor unit 10 and extend into the respective rooms, and the circulation pipe 30b1 The outdoor heat exchanger 13, the check valve 35, and the on-off valve 31 are provided in this order in the outdoor unit 10 from the switching port 12c side. A plurality of indoor units 20 are provided in parallel between the two circulation pipes 30b1 and 30b2 extending from the outdoor unit 10 to each room. Each indoor unit 20 is connected in series to an indoor heat exchanger 21, an electronic expansion valve 22 provided in series on the outdoor heat exchanger 13 side of the indoor heat exchanger 21, and the electronic expansion valve 22 in parallel. The checker valve 24 and the check valve 24 are arranged in a direction allowing the flow in the direction of flowing out from the indoor heat exchanger 21. Each indoor unit 20 has a check valve 24 side connected to the circulation line 30b1 and an indoor heat exchanger 21 side connected to the circulation line 30b2. Each indoor unit 20 is provided with an operating device (not shown) for starting / stopping the indoor unit 20, setting an air conditioning temperature, displaying an operation state, and the like.

  One end of the circulation line 30b3 connected to the bottom of the accumulator 17 to introduce the liquid refrigerant is connected to the other end of the circulation line 30b1 between the on-off valve 31 and the indoor unit 20 in the outdoor unit 10, A check valve 37 that allows a flow toward the circulation line 30b1 is provided in the circulation line 30b3 near the other end. A flow rate control valve 33 and a supercooling heat exchanger 18 are provided on the circulation line 30b3 from the accumulator 17 side at a position between the accumulator 17 and the check valve 37. The supercooling heat exchanger 18 is similar to the cooling water heat exchanger 16 in that the outer side of the conduit through which the refrigerant from the accumulator 17 passes is covered by a jacket, and the accumulator 17 and the flow control valve 33 are provided at one end of the jacket. Liquid phase refrigerant is introduced through the supercooling control valve 34 from between the other ends, and the other end of the jacket is connected to the circulation line 30b2.

  The supercooling heat exchanger 18 and the check valve 37 in the circulation line 30b3 are connected between the outdoor heat exchanger 13 and the check valve 35 in the circulation line 30b1 by the circulation line 30b4, and the circulation line 30b4. Is provided with a check valve 36 in such a direction as to allow the flow into the outdoor heat exchanger 13. A flow rate control valve 32 is provided in the circulation line 30b5 connecting the opening / closing valve 31 and the check valve 35 of the circulation line 30b1 to the nozzle portion 15a of the ejector 15. The flow rate control valve 32 is controlled by the control device 40 so that an optimum suction force is generated to suck the refrigerant introduced into the suction flow path 15b of the ejector 15 according to the operating state of the air conditioner. The refrigerant inflow amount to 15a is controlled.

  The control device 40 is based on the command input from the operating unit 41 and the operating unit of each indoor unit 20 and the temperature and pressure of each part detected by the temperature sensor and the pressure sensor (both not shown), etc. The operation of the air conditioner is controlled by controlling the four-way valve 12, the electronic expansion valve 22, the on-off valve 31, the flow control valve 32, the flow control valve 33, the supercooling control valve 34, and the like.

  Next, the operation of the engine-driven heat pump air conditioner of the above-described embodiment will be described. First, the operation during the cooling operation will be described with reference to FIG. In this cooling operation state, the control device 40 communicates the inlet port 12a of the four-way valve 12 with one switching port 12c and the outlet port 12b with the other switching port 12d, closes the on-off valve 31, and closes the cooling water heat exchanger. The cooling water supply from the gas engine to the 16 jackets is shut off, and the compressor 11 is driven by the gas engine. As shown by the arrow, the high-temperature and high-pressure gas-phase refrigerant compressed by the compressor 11 enters the outdoor heat exchanger 13 from the four-way valve 12 through the circulation line 30b1, and is cooled and liquefied by the outside air sent from the fan 13a. Is done. Since this high-pressure liquid-phase refrigerant is closed in the on-off valve 31 of the circulation line 30b1 and the check valve 36 is directed to prevent outflow, the ejector passes through the check valve 35, the flow control valve 32 and the strainer 500. 15 is introduced into the nozzle portion 15a and ejected from the suction channel 15b side toward the mixing channel 15c to reduce the pressure in the suction channel 15b.

  As will be described later, the vapor-phase refrigerant evaporated in the indoor heat exchanger 21 of the indoor unit 20 is sucked into the suction flow path 15b where the pressure is reduced, and the liquid-phase refrigerant from the nozzle portion 15a and the mixing flow path 15c. Then, the pressure is increased by the diffuser 15d and sent to the return line 30c connected to the end thereof. The refrigerant in which the gas phase and the liquid phase are mixed passes through the cooling water heat exchanger 16 and is separated into the gas phase and the liquid phase in the accumulator 17, and the separated gas phase refrigerant is returned to the suction port of the compressor 11. The control device 40 generates an optimum suction force in the suction flow path 15b of the ejector 15 according to the operating state of the air conditioner such as the number of indoor units 20 that are operating, the set temperature, the environmental temperature, and the pressure of each part. Thus, the amount of refrigerant flowing into the nozzle portion 15a is controlled by controlling the opening degree of the flow control valve 32 so that the improvement in cycle efficiency by the ejector 15 is maximized.

  The liquid refrigerant separated by the accumulator 17 is introduced into the circulation line 30b3, is supercooled by the supercooling heat exchanger 18, passes through the circulation line 30b1 from the check valve 37, and is depressurized by the electronic expansion valve 22 to be indoors. It enters into the heat exchanger 21 and is evaporated to cool it. The air sent into the room from the sirocco fan 21a is cooled by the indoor heat exchanger 21, whereby the room is cooled. The vapor phase refrigerant thus evaporated passes through the four-way valve 12 from the circulation pipe 30b2 and is sucked into the suction flow path 15b of the ejector 15 as described above. In this cooling operation, the space between the outdoor heat exchanger 13 and the check valve 35 is a part of the high pressure line, and the circulation line 30b3 is a part of the low pressure line. The flow of the refrigerant toward the former does not occur in the circulation conduit 30b4. In this cooling operation, the outdoor heat exchanger 13 serves as a condenser, and the indoor heat exchanger 21 serves as an evaporator.

  Next, FIG. 11 demonstrates the action | operation at the time of heating operation. In this heating operation state, the control device 40 communicates the inlet port 12a of the four-way valve 12 to the other switching port 12d and the outlet port 12b to one switching port 12c, opens the on-off valve 31, and opens the cooling water heat exchanger. The cooling water from the gas engine is circulated through the jacket 16, the flow control valve 33 controls the opening degree as described later, the supercooling control valve 34 is closed, and the compressor 11 is driven by the gas engine. As indicated by the arrow, the high-temperature and high-pressure gas-phase refrigerant compressed by the compressor 11 enters the indoor heat exchanger 21 of the indoor unit 20 from the four-way valve 12 through the circulation line 30b2, and is sent from the sirocco fan 21a. When the air passes through the indoor heat exchanger 21, it is heated by a high-temperature and high-pressure gas-phase refrigerant, thereby heating the room and cooling the gas-phase refrigerant to liquefy. The high-pressure liquid-phase refrigerant is sent to the circulation line 30b1 through the opened electronic expansion valve 22, the capillary 23, and the check valve 24, but the open / close valve 31 is opened, and the check valves 35 and 37 are opened. Is directed to block outflow, and is introduced into the nozzle portion 15a of the ejector 15 through the on-off valve 31, the flow control valve 32 and the strainer 500, and is ejected from the suction flow path 15b toward the mixing flow path 15c. The pressure in the suction channel 15b is reduced.

  As will be described later, the vapor-phase refrigerant evaporated in the outdoor heat exchanger 13 of the outdoor unit 10 is sucked into the suction flow path 15b due to this pressure drop, and the liquid-phase refrigerant from the nozzle portion 15a as in the case of the above-described cooling. In the mixing flow path 15c, the pressure is increased by the diffuser 15d, sent to the return pipe 30c, passed through the cooling water heat exchanger 16, and separated in the accumulator 17, the gas phase refrigerant sucked by the compressor 11 Return to port. This mixed refrigerant cools the gas engine when it passes through the cooling water heat exchanger 16 and becomes a high temperature, and is heat-exchanged with the cooling water passing through the water jacket, and a part of the waste heat of the gas engine is obtained. to recover. The control of the control device 40 with respect to the flow control valve 32 is the same as in the case of the cooling described above.

  The liquid-phase refrigerant separated by the accumulator 17 is introduced into the circulation line 30b3, but the supercooling control valve 34 is closed by the control device 40, and the flow control valve 33 has an opening degree according to the operating state of the air conditioner. Therefore, although it is not cooled by the supercooling heat exchanger 18, it is moderately depressurized, enters the outdoor heat exchanger 13 from the circulation line 30b4 through the check valve 36, and is sent from the fan 13a. Is evaporated by heating. The evaporated vapor phase refrigerant is sucked into the suction flow path 15b of the ejector 15 through the four-way valve 12 from the circulation pipe 30b1. In this heating operation, the circulation line 30b1 between the indoor heat exchanger 21 and the on-off valve 31 is a part of the high-pressure line, and the circulation line 30b3 is a part of the low-pressure line. There is no flow of refrigerant through the latter from the latter to the former. In this heating operation, the indoor heat exchanger 21 serves as a condenser, and the outdoor heat exchanger 13 serves as an evaporator. In this heating operation, the waste heat of the gas engine collected by the cooling water heat exchanger 16 is dissipated in the indoor heat exchanger 21, so that the heating capacity is improved.

  According to the engine-driven heat pump type air conditioner of the above-described embodiment, the refrigerant supply order to the outdoor heat exchanger 13 and the indoor heat exchanger 21 is switched by the four-way valve 12 so that the cooling operation or the heating operation is performed. Then, the refrigerant from the outdoor heat exchanger 13 or the indoor heat exchanger 21 serving as a condenser is introduced into the nozzle portion 15a of the ejector 15, and from the outdoor heat exchanger 13 or the indoor heat exchanger 21 serving as an evaporator. The refrigerant is introduced into the suction flow path 15b and the liquid phase refrigerant separated by the gas-liquid separator 17 is introduced into the outdoor heat exchanger 13 or the indoor heat exchanger 21 serving as the evaporator. Since it is connected to the circulation path 30, the refrigerant from the outdoor heat exchanger 13 and the indoor heat exchanger 21 flows through the ejector 15 in both the cooling operation and the heating operation. That is, the improvement of the cycle efficiency by the ejector 15 is performed in both the cooling operation and the heating operation.

(Other examples)
The first temperature sensor 303 detects the temperature TA upstream of the first flow control valve 302 and may be provided on the outlet side of the condenser 104. The second temperature sensor 305 detects the temperature TB downstream of the first flow control valve 302 and may be provided on the drive flow path 107 side of the ejectors 106 and 15. In addition, the present invention is not limited to the embodiments described above and shown in the drawings, and can be implemented with appropriate modifications within a range not departing from the gist.

  The present invention can be applied to an air conditioner that performs heating and / or cooling.

1 is a system diagram of an air conditioner according to Embodiment 1. FIG. It is sectional drawing of an ejector. It is a graph which shows the Mollier diagram of an air conditioning apparatus. It is a graph which shows a Mollier diagram. It is sectional drawing of the ejector which concerns on Example 1 and assembles a strainer. FIG. 6 is a cross-sectional view of an ejector according to Reference Example 1 . It is sectional drawing which concerns on the reference example 2 , and shows the state in which the mesh member is integrated. It is sectional drawing which concerns on the reference example 3 , and shows the state in which the fiber assembly is integrated. FIG. 6 is a system diagram of an air conditioner according to the second embodiment. FIG. 6 is a system diagram of an air conditioner according to the third embodiment. FIG. 6 is a system diagram of an air conditioner according to the third embodiment.

100 is a first refrigerant circulation path, 102 is a compressor, 104 is a condenser, 106 is an ejector, 107 is a drive channel, 108 is a nozzle section, 109 is a suction channel, 111 is a mixing channel, 114 is a separator, 200 is the second refrigerant circulation channel, 202 evaporator, 300 gas-liquid two-phase state stabilization means, the first flow control valve (flow rate adjustment mechanism) is 302, the first temperature sensor (first temperature detection means) 303, Reference numeral 305 denotes a second temperature sensor (second temperature detecting means), 500 denotes a strainer (homogenizing means), 510 denotes a mesh member (homogenizing means), and 520 denotes a fiber aggregate (homogenizing means).

Claims (4)

A compressor driven by a driving source to compress the refrigerant;
A condenser that condenses the high-pressure refrigerant compressed by the compressor to advance liquefaction;
Mixing and mixing the drive flow path for flowing the liquefied refrigerant, the suction flow path for sucking the suction flow by the refrigerant flowing through the drive flow path, the refrigerant flowing through the drive flow path, and the suction flow flowing through the suction flow path An ejector having a mixing flow path forming a flow;
A separator for separating the liquid phase and the gas phase of the mixed stream mixed by the ejector;
In an air conditioner comprising an evaporator for evaporating a liquid phase of a refrigerant having an inlet through which the liquid phase of the separator flows and an outlet connected to the suction flow path of the ejector,
Gas-liquid two-phase stabilization means for stably maintaining the refrigerant supplied from the outlet of the condenser to the inlet of the drive flow path of the ejector in a liquid-phase and gas-phase two-phase state, Between the outlet of the ejector and the inlet of the drive channel of the ejector, and
The homogenizing means for proceeding the homogenization of the two-phase state of the liquid phase and the gas phase of the refrigerant supplied from the condenser to the ejector via the gas-liquid two-phase state stabilizing means is the gas-liquid two-phase state. air conditioning apparatus characterized by being kicked set between the ejector and the stabilizing means.   2. The gas-liquid two-phase state stabilizing means according to claim 1, further comprising a flow rate variable mechanism that varies a flow rate of the refrigerant supplied from an outlet of the condenser to an inlet of a drive flow path of the ejector. An air conditioner characterized. According to claim 1 or 2, wherein the homogenizing means is an air conditioner which is a pore held member having pores.   4. The air conditioning apparatus according to claim 3, wherein the pore holding member is at least one of a mesh member, a fiber aggregate, or a particle aggregate.

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