JP4812665B2 - Ejector and refrigeration cycle apparatus - Google Patents

Description

  The present invention relates to an ejector and a refrigeration cycle apparatus, and more particularly to an refrigeration cycle apparatus such as an air conditioner, a refrigeration apparatus, and a hot water supply apparatus, and an ejector used for such a refrigeration cycle apparatus.

2. Description of the Related Art An ejector incorporated in a refrigeration cycle apparatus such as an air conditioner, a refrigeration apparatus, or a hot water supply apparatus is known. Such a refrigeration cycle apparatus raises the suction pressure of the compressor by sucking the evaporative gas by the suction action of the ejector and increasing the pressure, thereby reducing the compression ratio of the compressor and improving the efficiency of the refrigeration cycle. There is an effect to increase.
The conventional ejector is partly a double-pipe structure, and low-pressure driving fluid that is depressurized and accelerated from the single-hole nozzle body, which is the inner tube, and is ejected in the direction of the tube axis flows from the inner wall surface side of the outer tube The suction fluid (evaporator gas) is sucked. For this reason, (a) when a single-hole nozzle is used as the drive nozzle, the average droplet diameter of the droplet group constituting the drive fluid to be ejected from the suction section is increased.
(Ii) In addition, a droplet group having a large diameter is distributed in the central portion of the jet, and a relatively small droplet group is distributed in the peripheral portion of the jet, and the droplet diameter distribution is not uniform.
(Iii) Especially when the refrigerant state at the ejector inlet is a subcooled liquid or a saturated liquid, the phase change of the driving fluid passing through the throat of the driving nozzle may be delayed, and the conversion efficiency of the driving fluid into kinetic energy And the liquid flow may be delayed, resulting in a non-homogeneous distribution in which a large number of droplets having a relatively large diameter are present in the center of the jet.

(E) In such a case, the contact area between the driving fluid and the suction fluid is reduced, and the suction fluid cannot be sufficiently sucked, and the driving fluid and the suction fluid cannot be mixed homogeneously. A long mixing section is required from the initial mixing stage of the driving fluid and the suction fluid until the mixed layer develops. Therefore, sufficient mixing performance of the driving fluid and the suction fluid cannot be obtained, the pipe friction pressure loss increases, and the efficiency of the ejector decreases.
(O) In the vicinity of the inner wall surface, the boundary layer may become thick due to a large relative flow velocity difference between the high-speed driving fluid and the low-speed suction fluid, resulting in the formation of a backflow region. It increases and the efficiency of the ejector decreases.

  Therefore, in an ejector for a refrigeration cycle apparatus, a swirler formed in a spiral shape is arranged at the center of the mixing portion as a mixing promoting means, and the tip thereof is disposed so as to face the nozzle outlet. (For example, refer to Patent Document 1).

Japanese Patent Laid-Open No. 2001-200800 (page 2-3, FIG. 1)

However, the invention disclosed in Patent Document 1 has the following problems.
(B) It is difficult to actually place the swirler at the center of the mixing section (same as the axial center of the outer tube), and such a structure is likely to cause a large pressure loss. descend.
(B) As a result, in the refrigeration cycle in which the ejector is mounted, the ejector has a low efficiency, and therefore the suction fluid from the evaporator cannot be sufficiently sucked and pressurized by the ejector to be discharged. The refrigerant gas cannot be sufficiently sucked and the refrigeration capacity is reduced, or the suction pressure of the compressor cannot be sufficiently increased, and the efficiency of the refrigeration cycle cannot be improved.

The present invention has been made to solve the above-described problems. In an ejector mounted on a refrigeration cycle apparatus, the contact area between a driving fluid and a suction fluid is sufficiently increased, and a backflow is generated on the inner wall surface of the ejector. It aims at improving the efficiency of an ejector by suppressing generating, reducing pressure loss, and mixing uniformly over a short distance.
In addition, in a refrigeration cycle system equipped with an ejector, the efficiency of the compressor is improved by increasing the refrigeration capacity by increasing the ejector efficiency, and reducing the compression ratio of the compressor by increasing the suction pressure of the compressor. It aims to plan.

An ejector according to the present invention is an ejector having a cylindrical main body and a drive nozzle that is provided along the axial direction in the main body and ejects a drive fluid.
In the main body, a suction portion that sucks suction fluid by the drive fluid ejected from the drive nozzle, a mixing portion that mixes the ejected drive fluid and the sucked suction fluid, and the mixing portion are mixed. And a diffuser section for boosting the fluid
In order to atomize and rotate the liquid flow in the driving fluid flowing into the driving nozzle and the driving fluid flowing in the driving fluid from the driving fluid inlet, the cross-sectional area of the flow path in the driving nozzle A drive fluid atomization / swirl mechanism provided upstream from the throat where the smallest is provided, and a drive fluid ejection port for ejecting the atomized and swirled drive fluid, and
The drive fluid atomization / swirl mechanism is a cylindrical drive flow vane disposed in the drive nozzle, and a twisted groove channel is formed on the inner surface.

Therefore, the ejector according to the present invention sufficiently increases the contact area between the driving fluid and the suction fluid, suppresses the occurrence of backflow on the inner wall surface of the ejector, reduces the pressure loss, and is uniform over a short distance. Therefore, the efficiency of the ejector is improved.
In the refrigeration cycle apparatus in which the ejector according to the present invention is installed, since the refrigeration capacity is increased by the efficient ejector, the suction pressure of the compressor is increased, and the efficiency of the refrigeration cycle apparatus is improved.

[Embodiment 1: Refrigeration cycle apparatus]
FIG. 1 is a circuit configuration diagram illustrating a refrigeration cycle apparatus according to Embodiment 1 of the present invention. In FIG. 1, a refrigeration cycle apparatus 100 is, for example, a cooling apparatus that cools a room, and includes an outdoor unit 100a installed outdoors and an indoor unit 100b installed indoors, and the outdoor unit 100a receives cold heat. The medium to be cooled is transported to the indoor unit 100b, and the indoor unit 100b releases the cold heat to cool the room.

(Outdoor unit)
The outdoor unit 100a includes a compressor 1 that compresses the refrigerant, a heat source side heat exchanger 2 that releases the heat of the refrigerant compressed in the compressor 1, an ejector 3, and a first load side heat exchange that transmits cold heat to the indoor unit 100b side. 4, the gas-liquid separator 5, the expansion device 6 that decompresses the refrigerant, the second load-side heat exchanger 7 that transmits the cold to the indoor unit 100 b side, and the outdoor piping (shown by a thick solid line) that communicates these devices. Have a connection.
Refrigerants such as CO2, R404a, R410A, isobutane, and propane circulate in the outdoor pipe (outdoor unit 100a).

The heat source side heat exchanger 2 is a plate fin tube type heat exchanger composed of, for example, plate fins and pipes, and includes a blower 8 that blows outside air to the outer surface of the heat source side heat exchanger 2. The heat source side heat exchanger 2 performs heat exchange between the air around the outdoor unit 100a conveyed by the blower 8 and the refrigerant flowing in the pipe.
The first load-side heat exchanger 4 and the second load-side heat exchanger 7 are heat exchangers that exchange heat between a liquid that is a medium to be cooled, for example, water or brine, and a refrigerant. A type heat exchanger or a plate heat exchanger is used.
The expansion device 6 uses, for example, an electronic expansion valve whose opening degree is variably controlled.
The rotational speed of the compressor 1 and the opening degree of the expansion device 6 are controlled by a control device 9 constituted by a microcomputer or the like.

(Indoor unit)
The indoor unit 100b includes an indoor heat exchanger 10 and an indoor blower 11. In the indoor heat exchanger 10, between indoor air conveyed by the indoor blower 11 and liquid such as water and brine in indoor piping. Perform heat exchange. The room is cooled by exchanging heat of the cold transported by a medium to be cooled such as water or brine with room air.
In FIG. 1, the solid arrow indicates the flow of the refrigerant (outdoor unit 100a), the thick dotted arrow (indoor unit 100b) indicates the flow of water used as the medium to be cooled, the white arrow indicates the flow of air, and the thin dotted arrow indicates the control flow. The flow is shown.

(Ejector effect)
The operation of the refrigeration cycle apparatus 100 will be briefly described. In the outdoor unit 100a, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 dissipates heat into the air in the heat source side heat exchanger 2, condenses and liquefies, and flows into the ejector 3 as a high-pressure liquid refrigerant. . Then, part of the ejector 3 evaporates to become a gas-liquid state and flows into the gas-liquid separator 5.
The gas refrigerant separated in the gas-liquid separator 5 flows into the compressor 1 and circulates. On the other hand, the liquid refrigerant separated in the gas-liquid separator 5 flows into the expansion device 6 and is depressurized to become a low-temperature, low-pressure liquid refrigerant. Then, the refrigerant supplies cold heat to the indoor unit 100b side in the second load-side heat exchanger 7, becomes a gas refrigerant, and is sucked into the ejector 3.
As described above, by using the ejector 3 in the refrigeration cycle apparatus 100 (exactly, the outdoor unit 100a), the suction pressure of the compressor 1 can be increased, and the compression ratio becomes smaller, enabling highly efficient operation. (This will be described in detail separately.)

[Embodiment 2: Ejector]
2A and 2B illustrate an ejector according to Embodiment 2 of the present invention. FIG. 2A is a cross-sectional view schematically illustrating the configuration, and FIG. 2B is a pressure distribution on the central axis. FIG.
2A, the ejector 3 includes a substantially cylindrical outer cylinder 31 whose inner diameter varies in the tube axis direction, and a drive nozzle 32 inserted inside from one end surface of the outer cylinder 31. Yes.

(Drive nozzle)
The outer surface of the drive nozzle 32 has a cylindrical portion with a constant outer diameter (generally in the range of position X0-position X2) and a conical portion with a smaller outer diameter toward the tip (precisely, a truncated cone, generally at position X2-position X3). Range).
The inner surface is formed with a driving fluid inlet portion 36 into which a refrigerant serving as a driving fluid flows into a cylindrical portion (approximately the left side of the position X0). Then, the diameter is once reduced in a taper shape in the vicinity of the tip (position X1-position X2) to form the narrowest position X2, and then the diameter is increased in a taper shape to reach the driving fluid ejection port at the tip (position). X2-position X3).

(Outer cylinder)
The outer cylinder 31 is opposed to the cylindrical portion of the drive nozzle 32 in a cylindrical portion parallel to the cylindrical portion (generally in the range of position X0 to position X2), and thereafter in the ejection direction (in FIG. 2A). (The right side), the reduced portion (in the range of position X2 to position X4) once the inner diameter becomes smaller, the smaller diameter portion (in the range of position X4 to position X5) where the inner diameter does not change, and the inner diameter becomes larger as the ejection direction is reached. It has an enlarged portion (position X5-position X6) and a large-diameter portion (range of position X6-position X7) where the inner diameter does not vary.
Near the one end of the outer cylinder 31 (in the range of the position X0 to the position X1), a suction fluid inlet 37 for allowing the sucked fluid to flow is formed, and the diameter of the other end is large. A mixed fluid outlet 38 through which the mixed fluid flows is formed in the portion (position X7). In addition, although the number of the suction fluid inlet ports 37 is shown to be two at opposite positions, the present invention is not limited to this.

(Fluid flow path)
Therefore, a fluid flow path that flows in the right direction in the drawing along the tube axis direction (same as the longitudinal direction) is formed. That is, the fluid flow path includes a coolant flow path formed in the drive nozzle 32 through which the drive refrigerant flows, and a suction portion 33 formed in the outer cylinder 31 through which the fluid to be sucked flows (generally position X0 to position X3). ), A mixing portion 34 (range of position X3-position X5) through which the driving refrigerant and the suction fluid flow, and a diffuser portion 35 (range of position X5-position X6) where the mixed fluid is pressurized. Will be composed.
The driving fluid is a refrigerant flowing out from the heat source side heat exchanger 2, and the sucked fluid is a refrigerant flowing out from the second load side heat exchanger 7 (see FIG. 1).

(Pressure distribution)
In FIG. 2B, the vertical axis represents the pressure in the central axis, and the horizontal axis represents the position in the tube axis direction shown in FIG. In FIG. 2, the driving fluid flowing in from the driving fluid inlet 36 flows in the driving nozzle 32. In the drive nozzle 32, the drive refrigerant (position X1) having the pressure P1, which is the drive fluid, is depressurized to the pressure P2 (narrowest position X2) as the sound speed.
And it spouts to the mixing part 34 as a supersonic speed of the pressure P3 further from a drive nozzle exit (position X3). At this time, the suction fluid that has flowed in through the suction fluid inlet portion 37, here, the gas refrigerant, is sucked into the suction portion 33 and mixed in the mixing portion 34 (position X3 to position X5).
Further, the driving fluid and the suction fluid are mixed in the mixing unit 34 to become a gas-liquid two-phase refrigerant, the pressure is recovered and the pressure P5 is reached (position X5), and further in the diffuser unit 35 (position X5 to position X6). The pressure is increased (position X 6) and flows out to the mixed fluid outlet 38.

Therefore, the state of the refrigerant in the ejector 3 is reduced by the liquid or two-phase refrigerant at the driving fluid inlet 36 (position X0) and the nozzle at the driving nozzle outlet (position X3). Phase refrigerant.
On the other hand, in the outer cylinder 31, the suction fluid inlet portion 37 and the suction portion 33 have a gas refrigerant, while the mixing portion 34, the diffuser portion 35 and the ejector outlet portion 38 change in pressure as shown in FIG. It is a gas-liquid two-phase refrigerant.

(Refrigerant behavior)
FIG. 3 is a pressure-enthalpy diagram (Mollier diagram) showing the state of the circulating refrigerant for explaining the operation of the refrigeration cycle apparatus shown in FIG. In FIG. 3, the horizontal axis represents enthalpy, and I1 to I9 represent enthalpy values in the respective refrigerant states. The vertical axis is pressure,
Pc1 is the discharge pressure from the compressor 1,
Pe1 is the pressure at the outlet (position X6) of the ejector 3,
Pe2 indicates the pressure at the nozzle outlet (position X3) of the drive nozzle 32.

The gas refrigerant in the state R1 of the high-temperature / high-pressure Pc1 discharged from the compressor 1 is condensed and liquefied by releasing the heat to the air in the heat source side heat exchanger 2, and becomes a liquid refrigerant in the high-pressure state R2. The ejector 3 Into the driving fluid inlet 36.
The refrigerant having the pressure Pc1 flowing into the ejector 3 is branched by a refrigerant distributor (not shown) and then flows into each of the plurality of drive nozzles 32. And it will be in state R3 of pressure Pe2 at the exit (X3) of the drive nozzle 32, and will flow into the mixing part 34. FIG.
In the mixing part 34, after mixing with the refrigerant gas in the state R4 flowing from the suction fluid inlet part 37, the refrigerant in the state R5 recovers its pressure by the diffuser part 35, and becomes the state R6 at the pressure Pe1.

The refrigerant in the state R6 depressurized by the ejector flows into the first load side heat exchanger 4, takes heat from the medium to be cooled, and a part of the liquid refrigerant evaporates to become the state R7. Inflow.
The gas refrigerant in the state R8 separated by the gas-liquid separator 5 is supplied to the suction portion of the compressor 1 and circulates. On the other hand, the separated liquid refrigerant in the state R9 is depressurized by the expansion device 6, flows into the second load side heat exchanger 7, and evaporates to become a gas refrigerant in the state R4 to be a suction fluid inlet 37 of the ejector 3. Sucked into.

As described above, by using the ejector 3 in the refrigeration cycle apparatus 100, the suction pressure of the compressor 1 can be increased from Pe2 to Pe1, and the compression ratio becomes small, enabling highly efficient operation.
Here, the driving force of the ejector 3 is “enthalpy difference ΔH (= I2−I3)” between the enthalpy I3 at the time of isentropic expansion and the enthalpy I2 at the time of isentropic expansion in FIG. The larger the enthalpy difference ΔH is, the greater the effect of introducing the ejector 3 is. The enthalpy difference ΔH generally increases as the pressure difference ΔPc (= Pc1−Pe2) between the high pressure Pc1 and the low pressure Pe2 increases.

In general, the ejector efficiency includes the nozzle efficiency (En) when the pressure energy is converted into velocity energy by the drive nozzle 32, and the mixing when the velocity energy is mixed by the mixing unit 34 and the diffuser unit 35 and converted into pressure energy. -It is represented by the product (= En · Ek) with the diffuser efficiency (Ek).
The mixing / diffuser efficiency greatly contributes to the ejector efficiency. By promoting the mixing, the ejector efficiency can be effectively improved, and further the efficiency of the refrigeration cycle apparatus can be improved.

(Drive diversion vane)
4 and 5 schematically illustrate an ejector according to Embodiment 2 of the present invention. FIG. 4A is a cross-sectional view showing a state in which driving vanes are arranged. (B) of FIG. 4 is a perspective view showing a drive diversion vane, (c) is a cross-sectional view showing a state before the drive diversion vane is arranged, (d) of FIG. 4 is a schematic view showing refrigerant behavior, and FIG. a) is a sectional view showing a part of the configuration of the conventional product shown for reference, and (b) is a schematic diagram showing the refrigerant behavior of the conventional product. The same parts as those in FIG. 2 are denoted by the same reference numerals, and a part of the description is omitted.

5 (a), the drive diversion shown in the perspective view of FIG. 5 (b) is applied to the cylindrical portion of the drive nozzle 32a of the ejector 3a (on the upstream side of the position X1 where the diameter starts to be tapered in FIG. 2). A vane 51 is arranged. The drive flow vane 51 functions as a drive fluid atomization / swivel mechanism, and has a diameter of 50 mm or less and a length of 100 mm or less, and has a twisted groove channel 51 a on a cylindrical inner surface. Therefore, the liquid flow in the driving fluid flowing into the driving nozzle 32a can be atomized and swirled.
In addition, in order to change the degree of swirl, the driving flow vanes having various torsion flow paths (same as the groove flow paths) are replaced, so that as shown in FIG. A driving flow vane seat 52 is formed at the end.

Therefore, by ejecting the driving fluid from the driving nozzle 32a to which the driving flow vane 51 is mounted, atomization is facilitated because the liquid injection and the primary droplet are easily split into secondary droplets. That is, as shown in FIG. 5D, a droplet flow having a small diameter and a uniform diameter distribution and a large ejection angle is ejected, and the contact area between the driving fluid and the suction fluid can be sufficiently increased.
This increases the suction flow rate. Such behavior in the drive nozzle 32a promotes the phase change of the drive fluid flow particularly near the throat, and can also be expected to reduce the loss due to thermal non-equilibrium during the two-phase expansion process in the drive nozzle 32a. .

On the other hand, in the outer cylinder 31, the swirling flow of the driving fluid in the mixing unit 34 entrains the suction fluid, thereby promoting the mixing of the driving fluid and the suction fluid in the mixing unit 34. That is, the suction fluid does not flow along the vicinity of the pipe wall surface (see FIG. 5B), but as a relatively homogeneous mixed flow in which the driving fluid entrains the suction fluid as shown in FIG. 4D. Flowing.
And since a homogeneous mixed layer develops thickly, the mixing part 34 can be shortened, a pipe friction pressure loss can be reduced, and the pressure rise by an ejector can be increased. Furthermore, by improving the efficiency of the ejector, it is possible to increase the amount of increase in the compressor suction pressure when it is installed in the refrigeration cycle apparatus, to reduce the compression ratio, and to increase the refrigeration capacity. The cycle can be operated with high efficiency.

By the way, in the conventional product shown as a reference in FIG. 5, in the conventional single-hole drive nozzle 932 installed in the ejector 93, the division of the liquid flow is delayed and there are many droplets having a relatively large diameter at the center of the jet. Non-homogeneous droplet size distribution.
In such a case, the contact area between the driving fluid and the suction fluid is reduced, the suction fluid cannot be sufficiently sucked, and the driving fluid and the suction fluid cannot be mixed homogeneously. From the initial stage of mixing with the fluid until the mixing layer develops, a long mixing part is required, so that the mixing performance of the driving fluid and the suction fluid cannot be sufficiently obtained, the pipe friction pressure loss increases, There was a problem that the efficiency of the ejector decreased.
Further, in the vicinity of the inner wall surface of the outer cylinder 931, the boundary layer may become thick and peel due to a large relative flow velocity difference between the high-speed driving fluid and the low-speed suction fluid, and a backflow region may be formed. As a result, there is a problem that the pressure loss increases and the efficiency of the ejector decreases.

FIG. 10 is a pressure distribution diagram comparing an increase in the pressure increase width in the ejector 3 according to the second embodiment of the present invention with a case where a conventional single-hole nozzle is used.
In FIG. 10, the solid line indicates the case where the conventional single-hole nozzle 93 is used, and the broken line indicates the case where the drive nozzle 3 in the second embodiment is used.

  The fluid that flows into the ejector 3 uses R404A, R410A, CO2, isobutane, propane, or the like as a refrigerant, but is not limited thereto. The ejector 3 can be applied to all refrigeration cycles. The drive nozzle 32 may be a fixed nozzle or a variable nozzle. Furthermore, the present invention is applicable regardless of the size of the drive nozzle 32 and the outer cylinder 31 (for example, the mixing unit 34).

[Embodiment 3: Ejector]
(Swirl channel)
6 schematically illustrates an ejector according to Embodiment 3 of the present invention. FIG. 6A is a cross-sectional view showing a part of the configuration, and FIG. It is sectional drawing which shows a condition. The same parts as those in FIG. 2 are denoted by the same reference numerals, and a part of the description is omitted.
In the above-described second embodiment, the drive flow vane 51 is detachably installed at the inlet of the drive nozzle 32a as the drive fluid atomization / swirl mechanism, and the torsional flow path shape is different so that the degree of swirl can be adjusted. A drive diversion vane seat portion 52 is provided so that the diversion vane 51 can be replaced.
On the other hand, in the ejector 3b according to the third embodiment, as a drive fluid atomization / swirl mechanism, a tapered diameter-reduced portion at the tip of the drive nozzle 32b (hereinafter sometimes referred to as “wall surface of a tapered drive nozzle”). The swirl flow path 61 is provided as shown in FIG. The configuration of other parts is the same as that shown in FIG.

Therefore, also in the ejector 3b, the atomization is promoted as shown in FIG. 6B, so that the contact area between the driving fluid and the suction fluid is sufficiently increased, and the swirling flow of the driving fluid is generated by the suction fluid. The effect similar to that of the second embodiment is obtained such that the suction flow rate and the pressure increase in the ejector 3b are increased (see FIG. 10).
Thereby, the efficiency of the ejector 3b can be improved. Furthermore, the efficiency of the refrigeration cycle apparatus 100 can be improved by mounting the ejector 3b on the refrigeration cycle apparatus 100.

[Embodiment 4: Ejector]
(Auxiliary inflow hole)
FIG. 7 schematically illustrates an ejector according to Embodiment 4 of the present invention. FIG. 7A is a sectional view showing a part of the configuration, and FIG. Sectional drawing which shows a condition, (c) and (d) of FIG. 7 are circuit diagrams which show a mode that a fluid flows. The same parts as those in FIG. 2 are denoted by the same reference numerals, and a part of the description is omitted.
In FIG. 7, the drive nozzle 32c of the ejector 3c is formed with one or more auxiliary inflow holes 39 in contact with the inlet wall surface of the drive nozzle 32c. Therefore, a part of the total driving flow rate that flows in is ejected in a tangential direction through the auxiliary inflow hole 39, so that the liquid flow in the driving fluid can be atomized and swirled.
That is, as shown in FIG. 7 (d), a part of the entire driving flow rate that flows to the ejector 3 c flows into the auxiliary inflow passage 71 that is a bypass passage communicating with the auxiliary inflow hole 39. The degree of turning is adjusted by adjusting the flow rate with the valve 72 on the main inflow pipe side. Therefore, the ejector 3c can achieve the same effect as the ejector 3a (Embodiment 2) (see FIG. 10).
Moreover, if the efficient ejector 3c is installed in the refrigeration cycle apparatus 100, the suction pressure of the compressor 1 can be increased and the efficiency of the refrigeration cycle apparatus 100 can be improved.

[Embodiment 5: Ejector]
(Swirl channel for mixed fluid)
FIG. 8 is a cross-sectional view showing a part of a configuration for schematically explaining an ejector according to Embodiment 5 of the present invention. The same parts as those in FIG. 2 are denoted by the same reference numerals, and a part of the description is omitted.
In FIG. 8, in the ejector 3d, a mixed fluid swirl flow path 81 is provided on the inlet wall surface of the mixing portion of the outer cylinder 31d as a suction fluid swirl mechanism to swirl the suction fluid.
The mixed fluid swirling flow path 81 is provided on the inlet wall surface of the mixing section 34 with a length of 100 mm or less. By providing the mixed fluid swirl flow path 81 to swirl the suction fluid, the boundary layer is thinned, the occurrence of separation due to the development of the boundary layer is suppressed, and the recirculation vortex loss of the suction part flow is reduced or prevented Can do.
At the same time, fluid separation in the diffuser part 35 and the mixing part 34 can be reduced, and the pressure increase in the ejector is increased by reducing pressure loss and mixing uniformly over a short distance, thereby improving the efficiency of the ejector. Can be improved (see FIG. 10).
Further, if the efficient ejector 3d is installed in the refrigeration cycle apparatus 100, the suction pressure of the compressor 1 can be increased, and the efficiency of the refrigeration cycle apparatus 100 can be improved.

[Embodiment 6: Ejector]
(Auxiliary inflow hole)
FIG. 9 is a cross-sectional view showing a part of a configuration for schematically explaining an ejector according to Embodiment 6 of the present invention. The same parts as those in FIG. 2 are denoted by the same reference numerals, and a part of the description is omitted.
In FIG. 9, the ejector 3e is provided with an auxiliary outer cylinder 90 surrounding the outer cylinder 31e on the side where the drive nozzle 32 of the outer cylinder 31e is disposed. The outer cylinder 31e is a range surrounded by the auxiliary outer cylinder 90, and a plurality of auxiliary inflow holes 91 are opened in the mixing section 34, and the auxiliary inflow section is provided between the outer cylinder 31e and the auxiliary outer cylinder 90. 92 is formed. The suction inflow hole 91 is configured to open in the circumferential direction of the outer wall surface of the mixing unit in a direction perpendicular to or inclined with respect to the flow in the mixing unit 34.

That is, a part of the entire suction flow rate flowing to the suction part 33 is branched and flows into the auxiliary inflow part 92, and is ejected to the mixing part 34 through the auxiliary inflow hole 91. An effect of promoting mixing with the suction fluid is obtained.
Therefore, as in the fifth embodiment, the boundary layer is thinned, the occurrence of separation due to the development of the boundary layer can be suppressed, the recirculation vortex loss of the flow of the suction part 33 can be reduced or prevented, and the diffuser part 35 And the fluid separation in the mixing section 34 can be reduced, and the pressure loss is reduced and the mixture is uniformly mixed at a short distance, whereby the pressure increase width in the ejector 3e is increased and the efficiency of the ejector 3e can be improved (FIG. 10). reference).
Moreover, if the efficient ejector 3e is installed in the refrigeration cycle apparatus 100, the suction pressure of the compressor 1 can be increased and the efficiency of the refrigeration cycle apparatus 100 can be improved.

[Embodiment 1 to Embodiment 6]
As is clear from the above description, any of the ejectors 3a to 3e shown in the second to sixth embodiments can be installed in the refrigeration cycle apparatus 100 described in the first embodiment.
Further, the outer cylinders 31, 31d, 31e and the drive nozzles 32, 32a, 32b, 32c shown in the first to sixth embodiments can be appropriately combined.

  Since the present invention has the above-described configuration and the ejector efficiency is improved, the present invention can be widely used in various apparatuses using a refrigeration cycle, and can be widely used as various efficient refrigeration cycle apparatuses.

The circuit block diagram explaining the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention. Sectional drawing and pressure distribution figure explaining the ejector which concerns on Embodiment 2 of this invention. The Mollier diagram for demonstrating the driving | running operation | movement of the refrigerating-cycle apparatus shown in FIG. Sectional drawing etc. which demonstrate the ejector which concerns on Embodiment 2 of this invention. Sectional drawing etc. which show a part of conventional products shown for reference. Sectional drawing which illustrates typically the ejector which concerns on Embodiment 3 of this invention. Sectional drawing etc. which demonstrate typically the ejector which concerns on Embodiment 4 of this invention. Sectional drawing which illustrates typically the ejector which concerns on Embodiment 5 of this invention. Sectional drawing which illustrates typically the ejector which concerns on Embodiment 6 of this invention. The pressure distribution figure which compared the increase in the pressure rise width in the ejector shown in FIG.

Explanation of symbols

  1: compressor, 2: heat source side heat exchanger, 3: ejector (Embodiment 1), 3a: ejector (Embodiment 2), 3b: ejector (Embodiment 3), 3c: ejector (Embodiment) 4), 3d: ejector (Embodiment 5), 3e: ejector (Embodiment 6), 4: load side heat exchanger, 5: gas-liquid separator, 6: expansion device, 7: load side heat exchanger , 8: blower, 9: control device, 10: indoor heat exchanger, 11: indoor blower, 31: outer cylinder, 31a: outer cylinder (second embodiment), 31d: outer cylinder (fifth embodiment), 31e : Outer cylinder (Embodiment 6), 32: drive nozzle (Embodiment 1), 32a: drive nozzle (Embodiment 2), 32b: drive nozzle (Embodiment 3), 32c: drive nozzle (Embodiment) Form 4), 33: suction part, 34: mixing part, 35: diffuser part, 36 Driving fluid inlet section, 37: suction fluid inlet section, 38: mixed fluid outlet section, 39: auxiliary inflow hole (Embodiment 4), 51: driving flow vane (Embodiment 2), 51a: groove flow path, 52 : Vane seat for driving flow, 61: swirl flow path (Embodiment 3), 71: auxiliary inflow path, 72: valve, 81: swirl flow path for mixed fluid (Embodiment 5), 90: auxiliary outer cylinder ( Embodiment 6), 91: suction inflow hole, 91: auxiliary inflow hole, 92: auxiliary inflow part, 100: refrigeration cycle apparatus (Embodiment 1), 100a: outdoor unit, 100b: indoor unit, ΔH: enthalpy difference , ΔPc: pressure difference.

Claims (5)

An ejector having a cylindrical main body and a drive nozzle provided along the axial direction in the main body and ejecting a drive fluid,
In the main body, a suction portion that sucks suction fluid by the drive fluid ejected from the drive nozzle, a mixing portion that mixes the ejected drive fluid and the sucked suction fluid, and the mixing portion are mixed. And a diffuser section for boosting the fluid
In order to atomize and rotate the liquid flow in the driving fluid flowing into the driving nozzle and the driving fluid flowing in the driving fluid from the driving fluid inlet, the cross-sectional area of the flow path in the driving nozzle A drive fluid atomization / swirl mechanism provided upstream from the throat where the smallest is provided, and a drive fluid ejection port for ejecting the atomized and swirled drive fluid, and
The ejector according to claim 1, wherein the drive fluid atomization / swivel mechanism is a cylindrical drive flow vane disposed in the drive nozzle, and a torsional groove channel is formed on an inner surface thereof.   A drive having an annular stepped portion at an inner wall surface of the drive nozzle, a central portion having a circular cross section, a tapered portion that is reduced in diameter toward the driven fluid ejection port, and a connecting portion between the central portion and the tapered portion. 2. The ejector according to claim 1, wherein a diversion vane seat portion is formed, and the driving diversion vane is freely disposed at the stepped portion.   2. The ejector according to claim 1, wherein the drive fluid atomization / swivel mechanism is a torsion-shaped torsion channel formed on an inner wall surface of the drive nozzle. The drive fluid atomization / swirl mechanism is composed of one or more auxiliary inflow holes penetrating the wall surface of the drive nozzle, and an auxiliary inflow pipe communicating with the auxiliary inflow hole,
2. The ejector according to claim 1, wherein the driving fluid flows into the driving nozzle from the auxiliary inflow hole through the auxiliary inflow pipe together with the driving fluid flowing in from the driving fluid inflow port. A compressor that compresses the refrigerant;
A heat source side heat exchanger for releasing the heat held by the refrigerant compressed in the compressor;
The ejector according to any one of claims 1 to 4,
A gas-liquid separator that separates the refrigerant that has passed through the ejector into gas and liquid;
A throttling device for depressurizing the liquid refrigerant separated in the gas-liquid separator;
A first load-side heat exchanger for releasing cold heat held by the refrigerant that has passed through the expansion device;
A refrigeration cycle apparatus comprising:
The refrigerant that has passed through the heat source side heat exchanger is a drive fluid that flows into the drive nozzle of the ejector,
The refrigerant that has passed through the first load-side heat exchanger is a suction fluid that is sucked into the suction portion of the main body of the ejector,
The refrigeration cycle apparatus , wherein the gaseous refrigerant separated in the gas-liquid separator flows into the compressor .

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